Technical Field
[0001] The present invention relates to a screw compressor including a variable mechanism
whose internal volume ratio is variable.
Background Art
[0002] A hitherto known screw compressor includes a variable-internal-volume-ratio valve
(hereinafter referred to as variable Vi valve) as a slide valve that adjusts the timing
of starting discharge and by which internal volume ratio of the screw compressor is
variable. In such a screw compressor, the position of the variable Vi valve is adjusted
with a driving force applied from a driving device depending on the operating pressure
ratio. Herein, the internal volume ratio refers to the ratio between the volume of
a compression chamber at the completion of suction and the volume of the compression
chamber at the completion of discharge.
[0003] In general, if the screw compressor is operated at an appropriate compression ratio,
appropriate for the internal volume ratio thereof, no inappropriate compression loss
occurs. The compression volume is expressed as (discharge pressure)/(suction pressure).
However, if the screw compressor is operated at a compression ratio that is lower
than the appropriate compression ratio, gas that has been compressed to such a degree
as to open a discharge port is overcompressed to a degree higher than discharge pressure,
resulting in excessive compression work. Conversely, if the screw compressor is operated
at a compression ratio that is higher than the appropriate compression ratio, the
discharge port opens before discharge pressure is reached, resulting in an insufficient
compression that causes the backflow of the gas. Such situations both cause power
loss that leads to a reduction in efficiency. To suppress such a reduction in efficiency
due to power loss, the screw compressor needs to be operated at an optimum internal
volume ratio.
[0004] Accordingly, a screw compressor is known whose internal volume ratio is variable
by adjusting the position of a variable Vi valve (see Patent Literature 1, for example).
According to Patent Literature 1, the position of the variable Vi valve is adjusted
between two positions by opening or closing each of two solenoid valves, with no complicated
control mechanism for adjusting the position of the variable Vi valve. Specifically,
according to Patent Literature 1, a piston is coupled to the variable Vi valve through
a rod. Suction pressure or discharge pressure is switchably supplied to each of the
forward side and the backward side of the piston by using the two solenoid valves,
the sides being defined in the direction of movement of the piston. Since a pressure
difference is produced between the forward side and the backward side of the piston,
the piston is movable between two different positions. Thus, the position of the variable
Vi valve is adjustable between two levels.
Citation List
Patent Literature
[0005] Patent Literature 1: Japanese Patent No.
5881403
Summary of Invention
Technical Problem
[0006] According to Patent Literature 1, to adjust the position of the variable Vi valve
between two levels, two solenoid valves are necessary. To realize adjustment among
more levels, more number of solenoid valves are necessary.
[0007] The present invention is to overcome the above problem and provides a screw compressor
having a simple configuration with a reduced number of solenoid valves while realizing
a multi-level adjustment of internal volume ratio.
Solution to Problem
[0008] According to an embodiment of the present invention, there is provided a screw compressor
including a casing in which a discharge chamber and a suction chamber are provided;
a screw rotor in an outer peripheral surface of which a plurality of grooves forming
a compression chamber are provided, the screw rotor being rotatable in the casing;
a variable Vi valve movable in an axial direction of the screw rotor and whose stopping
position is switched in changing an internal volume ratio that is a ratio between
a volume of the compression chamber at completion of suction and a volume of the compression
chamber at completion of discharge; a driving device including a Vi piston coupled
to the variable Vi valve, and a driving cylinder that houses the Vi piston movably
in the driving cylinder; and a pressure-switching mechanism that switches pressure
to be introduced into the driving device. An inside of the driving cylinder is divided
by the Vi piston into two cylinder chambers. The driving device controls a position
of the variable Vi valve while moving the Vi piston by changing pressure in one of
the two cylinder chambers. The pressure-switching mechanism includes a solenoid valve
that switches whether to enable or disable introduction of discharge pressure from
the discharge chamber into the one cylinder chamber by opening or closing a first
passage through which the discharge chamber and the one cylinder chamber communicate
with each other; a switching cylinder communicating with the first passage extending
between the solenoid valve and the one cylinder chamber; a switching piston movably
housed in the switching cylinder; and a spring that is compressed with a movement
of the switching piston. An inside of the switching cylinder is divided by the switching
piston into a first switching cylinder chamber into which suction pressure is constantly
introduced and in which the spring is provided, and a second switching cylinder chamber
that communicates with the first passage. A second passage through which the first
switching cylinder chamber and the one cylinder chamber communicate with each other
is opened or closed depending on a position of the switching piston that receives
a spring force exerted by the spring. The pressure in the one cylinder chamber changes
when the first passage is opened or closed with opening or closing of the solenoid
valve while the second passage is opened or closed with the movement of the switching
piston.
Advantageous Effects of Invention
[0009] According to the embodiment of the present invention, the pressure to be supplied
to the Vi piston coupled to the variable Vi valve through the rod is changeable with
a single solenoid valve. Therefore, a screw compressor in which the internal volume
ratio is adjustable among a plurality of levels with a simple configuration can be
obtained.
Brief Description of Drawings
[0010]
[Fig. 1] Fig. 1 is a schematic diagram of a screw compressor according to Embodiment
1 of the present invention.
[Fig. 2] Fig. 2 is a schematic diagram illustrating a driving device and a pressure-switching
mechanism included in the screw compressor according to Embodiment 1 of the present
invention.
[Fig. 3] Fig. 3 is a schematic diagram illustrating the driving device and the pressure-switching
mechanism included in the screw compressor according to Embodiment 1 of the present
invention that operate at a high internal volume ratio.
[Fig. 4] Fig. 4 is a schematic diagram illustrating the driving device and the pressure-switching
mechanism included in the screw compressor according to Embodiment 1 of the present
invention that operate at a low internal volume ratio.
[Fig. 5] Fig. 5 is a schematic diagram illustrating a driving device and a pressure-switching
mechanism operate included in a screw compressor according to Embodiment 2 of the
present invention that operate at a high internal volume ratio.
[Fig. 6] Fig. 6 is a schematic diagram illustrating the driving device and the pressure-switching
mechanism included in the screw compressor according to Embodiment 2 of the present
invention that operate at a low internal volume ratio.
[Fig. 7] Fig. 7 is a schematic diagram illustrating a driving device and pressure-switching
mechanisms included in a screw compressor according to Embodiment 3 of the present
invention.
[Fig. 8] Fig. 8 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 3 of the present
invention that operate at a high internal volume ratio.
[Fig. 9] Fig. 9 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 3 of the present
invention that operate at a moderate internal volume ratio.
[Fig. 10] Fig. 10 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 3 of the present
invention that operate at a low internal volume ratio.
[Fig. 11] Fig. 11 is a schematic diagram illustrating a driving device and pressure-switching
mechanisms included in a screw compressor according to Embodiment 4 of the present
invention that operate at a high internal volume ratio.
[Fig. 12] Fig. 12 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 4 of the present
invention that operate at a moderate internal volume ratio.
[Fig. 13] Fig. 13 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 4 of the present
invention that operate at a low internal volume ratio.
[Fig. 14] Fig. 14 is a schematic diagram of a screw compressor according to Embodiment
5 of the present invention.
[Fig. 15] Fig. 15 is a schematic diagram of a screw compressor according to Embodiment
6 of the present invention.
Description of Embodiments
Embodiment 1
[0011] Fig. 1 is a schematic diagram of a screw compressor according to Embodiment 1 of
the present invention.
[0012] A screw compressor 1 according to Embodiment 1 is a single-screw compressor and includes
a cylindrical casing 2, a cylindrical screw rotor 5 housed in the casing 2, and a
motor 3 that drives the screw rotor 5 to rotate. The motor 3 includes a stator 3a
provided in contact with and fixed to the inner wall of the casing 2, and a motor
rotor 3b provided on the inner side of the stator 3a. The motor 3 may be of an inverter
type in which the rotation speed is controlled by an inverter, or a constant-speed
type in which the rotation speed is constant.
[0013] The screw rotor 5 and the motor rotor 3b are positioned coaxially with each other
and are both fixed to a screw shaft 4. The screw rotor 5 has a plurality of helical
screw grooves 5a in the outer peripheral surface thereof. The screw rotor 5 is coupled
to the motor rotor 3b fixed to the screw shaft 4, thereby being driven to rotate.
Spaces in the screw grooves 5a provided in the screw rotor 5 are enclosed by the inner
peripheral surface of the casing 2 and a pair of gate rotors (not illustrated) that
are in mesh with the screw grooves 5a, thereby forming a compression chamber 6.
[0014] The inside of the casing 2 is divided by a partition (not illustrated) into a discharge-pressure
side and a suction-pressure side. The discharge-pressure side has a discharge chamber
7 and a discharge port 8 provided in the discharge chamber 7. A suction chamber 16
is provided at the suction-pressure side . Discharge pressure is a pressure exerted
by refrigerant compressed in the compression chamber 6 and discharged from the compression
chamber 6. Suction pressure is a pressure exerted by refrigerant taken into the compression
chamber 6. The relationship between discharge pressure and suction pressure is that
discharge pressure is greater than suction pressure.
[0015] A pair of variable Vi valves 9 that are movable in the axial direction of the screw
shaft 4 are provided between the inner peripheral surface of the casing 2 and the
outer peripheral surface of the screw rotor 5. The variable Vi valves 9 form part
of the discharge port 8 and is coupled to a driving device 11 through a rod 10. In
Fig. 1, only the driving device 11 coupled to one of the variable Vi valves 9 is illustrated,
and another driving device 11 coupled to the other variable Vi valve 9 is not illustrated.
[0016] The driving device 11 is driven with gas pressure and includes a cylinder 12 and
a Vi piston 13 housed in the cylinder 12. The Vi piston 13 is movable in the axial
direction in the cylinder 12. The Vi piston 13 is coupled to the variable Vi valve
9 through the rod 10, thereby being movable in the axial direction in the cylinder
12. The Vi piston 13 corresponds to the Vi piston or the first Vi piston according
to the present invention.
[0017] Embodiment 1 includes a pressure-switching mechanism 21 illustrated in Fig. 2 to
be referred to below. The pressure-switching mechanism 21 switches the pressure to
be introduced into the driving device 11 and has a simpler configuration than a mechanism
including two solenoid valves.
[0018] The screw compressor 1 further includes a controller 50 (see Fig. 1) that opens and
closes a solenoid valve 27, to be described below, included in the pressure-switching
mechanism 21. The controller 50 may be a piece of hardware such as a circuit device
that realizes the function thereof, or a combination of an arithmetic device such
as a CPU and a piece of software to be executed thereon.
[0019] Referring to Fig. 2, configurations of the driving device 11 and the pressure-switching
mechanism 21 will now be described. Hereinafter, an element "passage" may be provided
as a hole in the wall of the casing 2 or the cylinder 12, or as a pipe.
[0020] Fig. 2 is a schematic diagram illustrating the driving device and the pressure-switching
mechanism included in the screw compressor according to Embodiment 1 of the present
invention. In Fig. 2, the right side of the variable Vi valve 9 is under suction pressure,
and the left side of the variable Vi valve 9 is under discharge pressure.
[0021] First, the variable Vi valve 9 will be described. The variable Vi valve 9 includes
a valve body 9a, a guide portion 9b, and a coupling portion 9c. The valve body 9a
and the guide portion 9b are coupled to each other through the coupling portion 9c.
One end of the rod 10 is coupled to a driving-device-side end 9h of the guide portion
9b. The other end of the rod 10 is coupled to an end face of the Vi piston 13 that
is nearer to the variable Vi valve 9. A space between a discharge-port-side end 9d
of the valve body 9a and a discharge-port-side end 9e of the guide portion 9b forms
a discharge air gap 9f communicating with the discharge port 8.
[0022] The space in the cylinder 12 of the driving device 11 is divided by the Vi piston
13 into a cylinder chamber 14a on a variable-Vi-valve side (the right side in the
drawing) and a cylinder chamber 14b on the other side (the left side in the drawing).
The cylinder 12 corresponds to the driving cylinder according to the present invention.
The cylinder chamber 14a corresponds to the first cylinder chamber according to the
present invention. The cylinder chamber 14b corresponds to the second cylinder chamber
according to the present invention.
[0023] The cylinder 12 has a pressure-introducing hole 114a at the cylinder chamber 14a,
and another pressure-introducing hole 114b and a pressure-releasing hole 114c at the
cylinder chamber 14b. The cylinder chamber 14a communicates with the discharge chamber
7, illustrated in Fig. 1, through the pressure-introducing hole 114a and a passage
15a. Furthermore, discharge pressure is constantly introduced from the discharge chamber
7 into the cylinder chamber 14a.
[0024] The cylinder chamber 14b is connected to the pressure-switching mechanism 21 through
the pressure-introducing hole 114b and a passage 15b. The pressure-switching mechanism
21 switches to enable or disable the introduction of discharge pressure into the cylinder
chamber 14b. The cylinder chamber 14b communicates with the discharge chamber 7 through
the pressure-switching mechanism 21 and a passage 30. The pressure-switching mechanism
21 switches to enable or disable the introduction of discharge pressure from the discharge
chamber 7 into the cylinder chamber 14b. The passage 30 includes the passage 15b,
a passage 28c, and a passage 28d and corresponds to the first passage according to
the present invention.
[0025] The cylinder chamber 14b communicates with the suction chamber 16 through the pressure-releasing
hole 114c and a passage 15c. The passage 15c is provided at a halfway position thereof
with an expansion mechanism 15ca. The expansion mechanism 15ca is provided for preventing
the pressure in the cylinder chamber 14b from being released through the pressure-releasing
hole 114c toward the suction-chamber side. Specifically, the expansion mechanism 15ca
is, for example, a capillary tube or an orifice. The expansion mechanism 15ca corresponds
to the second expansion mechanism according to the present invention.
[0026] The pressure-switching mechanism 21 includes the solenoid valve 27, a cylinder 22,
a switching piston 23, a rod 24 coupled to the switching piston 23, and a spring 25
that is compressed with the movement of the switching piston 23. The cylinder 22 houses
the switching piston 23 such that the switching piston 23 is movable in the axial
direction. The spring 25 is provided around the rod 24 and is positioned in a cylinder
chamber 26a to be described below. When the spring 25 has a natural length, the switching
piston 23 is positioned as illustrated in Fig. 3 to be referred to below. The switching
piston 23 and the rod 24 do not necessarily need to be separate components and may
be provided as an integrally molded component. The pressure-switching mechanism 21
corresponds to the first mechanism according to the present invention.
[0027] As described above, the pressure-switching mechanism 21 includes a single solenoid
valve and has a simpler configuration than a mechanism including two solenoid valves.
Specifically, a solenoid valve not only includes a cylinder, a piston, a rod, a spring,
and so forth but also requires a solenoid unit that converts electrical energy for
opening and closing the solenoid valve with a magnetic force into a mechanical motion.
The solenoid unit includes a coil, a yoke, a sleeve, a core, and a plug nut. The core
is formed of a movable iron core of a plunger. The plug nut is formed of a fixed iron
core. Hence, the mechanism including two solenoid valves tends to be expensive. In
contrast, the pressure-switching mechanism 21 includes a single solenoid valve and
other elements, namely, the cylinder 22, the switching piston 23, the rod 24, and
the spring 25. Therefore, the pressure-switching mechanism 21 can be made less expensive
than the mechanism including two solenoid valves.
[0028] Now, the pressure-switching mechanism 21 will be described in detail.
[0029] The solenoid valve 27 opens to form the passage 28d through which the discharge chamber
7 and the cylinder 22 communicate with each other, and closes to block the passage
28d, and is switched to open to enable the introduction of discharge pressure from
the discharge chamber 7 into a cylinder chamber 26b, to be described below, of the
cylinder 22, or disable the introduction of discharge pressure from the discharge
chamber 7 into the cylinder chamber 26b. The cylinder chamber 26b communicates with
the cylinder chamber 14b of the driving device 11 through the passage 28c. Therefore,
it can also be said that the solenoid valve 27 switches whether to enable or disable
the introduction of discharge pressure from the discharge chamber 7 into the cylinder
chamber 14b.
[0030] The inside of the cylinder 22 is divided by the switching piston 23 into the cylinder
chamber 26a and the cylinder chamber 26b. The cylinder 22 has a pressure-introducing
hole 214a at the cylinder chamber 26a, and a pressure-introducing hole 214d and a
pressure-releasing hole 214c at the cylinder chamber 26b. Furthermore, the cylinder
22 has a pressure-releasing hole 214b that is opened or closed depending on the position
of the switching piston 23. The cylinder 22 corresponds to the switching cylinder
according to the present invention. The cylinder chamber 26a corresponds to the first
switching cylinder chamber according to the present invention. The cylinder chamber
26b corresponds to the second switching cylinder chamber according to the present
invention.
[0031] The cylinder chamber 26a communicates with the suction chamber 16, illustrated in
Fig. 1, through the pressure-introducing hole 214a and a passage 28a, and suction
pressure is constantly introduced from the suction chamber 16 into the cylinder chamber
26a. The cylinder chamber 26b communicates with the discharge chamber 7, illustrated
in Fig. 1, through the pressure-introducing hole 214d, the passage 28d, and the solenoid
valve 27. When the solenoid valve 27 is open, discharge pressure is introduced into
the cylinder chamber 26b.
[0032] The pressure-releasing hole 214b communicates with the passage 28c through a passage
28b. An expansion mechanism 28ba is provided at the passage 28b. The expansion mechanism
28ba is provided for preventing the introduction of discharge pressure in the cylinder
chamber 14b into the cylinder chamber 26a when the state of the solenoid valve 27
is switched from open to close. The expansion mechanism 28ba is a component such as
an orifice or a capillary tube. The passage 28b corresponds to the second passage
according to the present invention. The expansion mechanism 28ba corresponds to the
first expansion mechanism according to the present invention.
[0033] Now, an operation of the variable Vi valve 9 will be described, in association with
piston motions of the driving device 11 and the pressure-switching mechanism 21. In
Embodiment 1, the value of the internal volume ratio (hereinafter referred to as Vi
value) is settable between two levels of high and low. The internal volume ratio refers
to the ratio between the volume of the compression chamber at the completion of suction
and the volume of the compression chamber at the completion of discharge.
(1) Operation with High Vi Value
[0034] Fig. 3 is a schematic diagram illustrating the driving device and the pressure-switching
mechanism included in the screw compressor according to Embodiment 1 of the present
invention that operate at a high internal volume ratio. In Fig. 3 and other drawings
to be referred to below, the solid-black solenoid valve indicates that the solenoid
valve is in the "closed" state, and the solid-white solenoid valve indicates that
the solenoid valve is in the "open" state. Furthermore, the arrow illustrated in each
of Fig. 3 and other drawings to be referred to below indicates the direction of movement
of the Vi piston.
[0035] When the Vi value is high, the solenoid valve 27 is closed. Accordingly, the driving
device 11 causes the variable Vi valve 9 to move leftward as indicated by the arrow
illustrated in the drawing. Thus, the timing of opening the discharge port 8 is slowed.
[0036] First, an operation of the pressure-switching mechanism 21 will be described. When
the Vi value is high, the solenoid valve 27 is closed. Accordingly, the pressure in
the cylinder chamber 26b is made equal to the pressure in the cylinder chamber 14b
of the driving device 11 that communicates with the cylinder chamber 26b through the
passage 28c. Specifically, immediately after the state of the solenoid valve 27 is
switched from being open to being closed, the cylinder chamber 26b and the cylinder
chamber 14b are under discharge pressure. However, since the cylinder chamber 14b
communicates with the suction chamber 16 through the expansion mechanism 15ca, the
pressure in the cylinder chamber 26b and the cylinder chamber 14b becomes closer to
suction pressure with time. Furthermore, suction pressure is constantly introduced
into the cylinder chamber 26a. Therefore, as the pressure in the cylinder chamber
26b becomes closer to suction pressure, the switching piston 23 is moved toward the
cylinder chamber 26b by the spring 25. Consequently, the pressure-releasing hole 214b
is opened.
[0037] When the pressure-releasing hole 214b is opened, the cylinder chamber 26a and the
cylinder chamber 14b come to communicate with each other through the passage 28b and
the passage 15b. Accordingly, the cylinder chamber 14b of the driving device 11 comes
to have suction pressure, as with the cylinder chamber 26a. Thus, when the solenoid
valve 27 is closed, the pressure-switching mechanism 21 introduces suction pressure
into the cylinder chamber 14b.
[0038] Now, operations of the driving device 11 and the variable Vi valve 9 will be described.
The cylinder chamber 14a is coupled to the discharge chamber 7. Therefore, discharge
pressure is constantly introduced into the cylinder chamber 14a. Hence, there is a
pressure difference in the cylinder 14, and the Vi piston 13 therefore tends to move
leftward in the drawing.
[0039] Regarding two ends, defined in the moving direction, of the variable Vi valve 9 coupled
to the Vi piston 13, a suction-side end 9g of the valve body 9a is under suction pressure,
and the driving-device-side end 9h of the guide portion 9b is under discharge pressure.
Furthermore, the discharge-port-side end 9d of the valve body 9a is under discharge
pressure obtained immediately after the discharge, and the discharge-port-side end
9e of the guide portion 9b is under discharge pressure that is equal to but acts in
the opposite direction to the pressure acting on the discharge-port-side end 9d. Hence,
loads applied to the discharge-port-side end 9d and the discharge-port-side end 9e
cancel each other out. Consequently, the variable Vi valve 9 tends to move rightward
in the drawing because of the difference between the pressures acting on the driving-device-side
end 9h and the suction-side end 9g.
[0040] The area of each of the front and rear surfaces of the Vi piston 13, the front and
rear directions being defined in the moving direction is greater than the area of
the driving-device-side end 9h at which the variable Vi valve 9 receives discharge
pressure. Hence, the Vi piston 13 and the variable Vi valve 9 move leftward in the
drawing because of the difference between the pressures received by the front and
rear surfaces of the Vi piston 13 that are defined in the moving direction. The variable
Vi valve 9 stops at a position where the Vi piston 13 comes into contact with the
wall of the cylinder chamber 14b. Therefore, the variable Vi valve 9 is accurately
positioned for the high Vi value.
(2) Operation with Low Vi Value
[0041] Fig. 4 is a schematic diagram illustrating the driving device and the pressure-switching
mechanism included in the screw compressor according to Embodiment 1 of the present
invention that operate at a low internal volume ratio.
[0042] When the Vi value is low, the solenoid valve 27 is open. Accordingly, the driving
device 11 causes the variable Vi valve 9 to move rightward as indicated by the arrow
illustrated in the drawing. Thus, the timing of opening the discharge port 8 is advanced.
[0043] First, an operation of the pressure-switching mechanism 21 will be described. When
the Vi value is low, the solenoid valve 27 is open. Accordingly, the cylinder chamber
26b is under discharge pressure. Furthermore, the cylinder chamber 26a is under suction
pressure that is introduced constantly thereinto, whereas the switching piston 23
is under suction pressure and a spring force that act in a direction opposite to the
direction of a force applied from the cylinder chamber 26b. Such a relationship among
the forces acting on the switching piston 23 causes the switching piston 23 to move
toward the cylinder chamber 26a and thus close the pressure-releasing hole 214b.
[0044] Since the pressure-releasing hole 214b is closed, the cylinder chamber 14b of the
driving device 11 communicates with the cylinder chamber 26b of the pressure-switching
mechanism 21 without communicating with the cylinder chamber 26a, and comes to receive
discharge pressure as with the cylinder chamber 26b. Note that the cylinder chamber
14b communicates with the suction chamber 16 through the pressure-releasing hole 114c
and the passage 15c. However, since the expansion mechanism 15ca is provided at the
passage 15c , the inside of the cylinder chamber 14b is kept under discharge pressure
while the solenoid valve 27 is open.
[0045] Thus, when the solenoid valve 27 is open, the pressure-switching mechanism 21 introduces
discharge pressure into the cylinder chamber 14b.
[0046] Now, operations of the driving device 11 and the variable Vi valve 9 will be described.
The cylinder chamber 14a is coupled to the discharge chamber 7, and discharge pressure
is constantly introduced into the cylinder chamber 14a. Hence, there is no pressure
difference in the cylinder 14.
[0047] Regarding the variable Vi valve 9 coupled to the Vi piston 13, the suction-side end
9g of the valve body 9a is under suction pressure, and the driving-device-side end
9h of the guide portion 9b is under discharge pressure. Furthermore, the discharge-port-side
end 9d of the valve body 9a is under discharge pressure obtained immediately after
the discharge, and the discharge-port-side end 9e of the guide portion 9b is under
discharge pressure that is equal to but acts in the opposite direction to the pressure
acting on the discharge-port-side end 9d. Hence, loads applied to the discharge-port-side
end 9d and the discharge-port-side end 9e cancel each other out.
[0048] Since there is no pressure difference in the cylinder 14, the variable Vi valve 9
moves rightward in the drawing because of the difference between the discharge pressure
acting on the driving-device-side end 9h and the suction pressure acting on the suction-side
end 9g. The variable Vi valve 9 stops at a position where the suction-side end 9g
comes into contact with the wall of the casing 2. Therefore, the variable Vi valve
9 is accurately positioned for the low Vi value.
[0049] As described above, according to Embodiment 1, the position of the variable Vi valve
9 is controlled by changing the pressure in one of the cylinder chamber 14a and the
cylinder chamber 14b by opening or closing the single solenoid valve 27. In the above
case, the pressure in the cylinder chamber 14b is changed. The change of the pressure
in the cylinder chamber 14b is realized as follows. The passage extending from the
discharge chamber 7 to the cylinder chamber 14b is allowed to communicate or blocked
by opening or closing the solenoid valve 27. Accordingly, the switching piston 23
moves against the spring force exerted by the spring 25 in such a manner as to allow
the passage 28b that is under suction pressure to communicate or block the passage
28d. In other words, the pressure in the cylinder chamber 14b can be changed by controlling
the movement of the switching piston 23 with a simple mechanism utilizing the difference
between the discharge pressure and the suction pressure that act on the switching
piston 23 and the spring force exerted by the spring 25. Hence, the pressure in the
cylinder chamber 14b can be changed without using two solenoid valves. Consequently,
a screw compressor that is inexpensive and has a simple configuration can be obtained.
[0050] Furthermore, compared with the configuration according to Patent Literature 1 in
which the internal volume ratio is adjustable between two levels, the number of solenoid
valves to be controlled is reduced from two to one. Therefore, the process of controlling
the solenoid valve is also simplified.
Embodiment 2
[0051] Embodiment 2 of the present invention is different from Embodiment 1 in that the
pressure-switching mechanism 21 is connected to the cylinder chamber 14a instead of
the cylinder chamber 14b. More specifically, the pressure-switching mechanism 21 is
connected to the pressure-introducing hole 114a, and the pressure-introducing hole
114b is made to communicate with the suction chamber 16.
[0052] Now, an operation of the variable Vi valve 9 according to Embodiment 2 will be described.
As with Embodiment 1, the Vi value is settable between two levels of high and low.
(1) Operation with High Vi Value
[0053] Fig. 5 is a schematic diagram illustrating a driving device and a pressure-switching
mechanism included in a screw compressor according to Embodiment 2 of the present
invention that operate at a high internal volume ratio.
[0054] When the Vi value is high, the driving device 11 causes the variable Vi valve 9 to
move leftward as indicated by the arrow illustrated in the drawing. Thus, the timing
of opening the discharge port 8 is slowed.
[0055] Specifically, when the Vi value is high, the solenoid valve 27 is open. Accordingly,
the inside of the cylinder chamber 14a is under discharge pressure. On the other hand,
the cylinder chamber 14b is coupled to the suction chamber 16, and suction pressure
is constantly introduced into the cylinder chamber 14b. Hence, there is a pressure
difference in the cylinder 12, and the Vi piston 13 therefore tends to move leftward
in the drawing.
[0056] Regarding the variable Vi valve 9 coupled to the Vi piston 13, the suction-side end
9g of the valve body 9a is under suction pressure, and the driving-device-side end
9h of the guide portion 9b is under discharge pressure. Furthermore, the discharge-port-side
end 9d of the valve body 9a is under discharge pressure obtained immediately after
the discharge, and the discharge-port-side end 9e of the guide portion 9b is under
discharge pressure that is equal to but acts in the opposite direction to the pressure
acting on the discharge-port-side end 9d. Hence, loads applied to the discharge-port-side
end 9d and the discharge-port-side end 9e cancel each other out. Consequently, the
variable Vi valve 9 tends to move rightward in the drawing because of the difference
between the pressures acting on the driving-device-side end 9h and the suction-side
end 9g. However, as described above, since the area of the Vi piston 13 is set greater
than the area of the driving-device-side end 9h of the variable Vi valve 9, the Vi
piston 13 and the variable Vi valve 9 move leftward in the drawing because of the
difference between the pressures applied to the two surfaces of the Vi piston 13.
The variable Vi valve 9 stops at a position where the Vi piston 13 comes into contact
with the wall of the cylinder chamber 14b. Therefore, the variable Vi valve 9 is accurately
positioned for the high Vi value.
(2) Operation with Low Vi Value
[0057] Fig. 6 is a schematic diagram illustrating the driving device and the pressure-switching
mechanism included in the screw compressor according to Embodiment 2 of the present
invention that operate at a low internal volume ratio.
[0058] When the Vi value is low, the driving device 11 causes the variable Vi valve 9 to
move rightward as indicated by the arrow illustrated in the drawing. Thus, the timing
of opening the discharge port 8 is advanced.
[0059] Specifically, the solenoid valve 27 is closed. Accordingly, the inside of the cylinder
chamber 14a is under suction pressure. On the other hand, the cylinder chamber 14b
is coupled to the suction chamber 16, and suction pressure is constantly introduced
into the cylinder chamber 14b. Hence, there is no pressure difference in the cylinder
12.
[0060] Regarding the variable Vi valve 9 coupled to the Vi piston 13, the suction-side end
9g of the valve body 9a is under suction pressure, and the driving-device-side end
9h of the guide portion 9b is under discharge pressure. Furthermore, the discharge-port-side
end 9d of the valve body 9a is under discharge pressure obtained immediately after
the discharge, and the discharge-port-side end 9e of the guide portion 9b is under
discharge pressure that is equal to but acts in the opposite direction to the pressure
acting on the discharge-port-side end 9d. Hence, loads applied to the discharge-port-side
end 9d and the discharge-port-side end 9e cancel each other out.
[0061] Since there is no pressure difference in the cylinder 14, the variable Vi valve 9
moves rightward in the drawing because of the difference between the discharge pressure
acting on the driving-device-side end 9h and the suction pressure acting on the suction-side
end 9g. The variable Vi valve 9 stops at a position where the suction-side end 9g
comes into contact with the wall of the casing 2. Therefore, the variable Vi valve
9 is accurately positioned for the low Vi value.
[0062] Embodiment 2 is different from Embodiment 1 in that the pressure-switching mechanism
21 is connected to the cylinder chamber 14a instead of the cylinder chamber 14b, and
can produces the same advantageous effects as Embodiment 1.
Embodiment 3
[0063] While Embodiment 1 and Embodiment 2 concern a case where the Vi value is variable
between two levels of high and low, Embodiment 3 concerns a case where the Vi value
is variable among three levels of high, moderate, and low.
[0064] Fig. 7 is a schematic diagram illustrating a driving device and pressure-switching
mechanisms included in a screw compressor according to Embodiment 3 of the present
invention. Elements that are common to those illustrated in Fig. 2 are denoted by
corresponding ones of the reference numerals, and description of such elements is
omitted.
[0065] The screw compressor according to Embodiment 3 includes a pressure-switching mechanism
31, in addition to the elements according to Embodiment 1. Furthermore, the cylinder
chamber 14b of the driving device 11 is provided with a Vi piston 39, an interlocked
piston 40, a coupling portion 41, and a positioning wall 42, in addition to the elements
according to Embodiment 1. The cylinder chamber 14b is divided by the Vi piston 39
into two cylinder chambers. Specifically, the cylinder chamber 14b includes a cylinder
chamber 14c provided between the Vi piston 39 and the Vi piston 13, and a cylinder
chamber 14d provided opposite to the cylinder chamber 14c. The Vi piston 39 corresponds
to the second Vi piston according to the present invention.
[0066] In Embodiment 1, the pressure-switching mechanism 21 switches the pressure to be
introduced into the cylinder chamber 14b. In Embodiment 3, the pressure to be introduced
into the cylinder chamber 14c included in the cylinder chamber 14b is switched. The
cylinder chamber 14a corresponds to the first cylinder chamber according to the present
invention. The cylinder chamber 14c corresponds to the second cylinder chamber according
to the present invention. The cylinder chamber 14d corresponds to the third cylinder
chamber according to the present invention.
[0067] The Vi piston 39 is coupled to the interlocked piston 40 through the coupling portion
41. The positioning wall 42 extending in a direction orthogonal to the direction of
movement of the Vi piston 39 is provided between the Vi piston 39 and the interlocked
piston 40. The positioning wall 42 has a hole 42a. The coupling portion 41 movably
extends through the hole 42a. Therefore, the Vi piston 39 is movable together with
the interlocked piston 40 in the cylinder chamber 14b.
[0068] The Vi piston 39 is positioned when the Vi piston 39 is stopped by coming into contact
with the positioning wall 42 or when the Vi piston 39 moving away from the positioning
wall 42 is stopped because the interlocked piston 40 comes into contact with the positioning
wall 42. The Vi piston 13 and the Vi piston 39 are movable independently of each other
in the cylinder 12.
[0069] The cylinder 12 has a pressure-introducing hole 114e and a pressure-releasing hole
114f at the cylinder chamber 14d. The cylinder chamber 14d is connected to the pressure-switching
mechanism 31 through the pressure-introducing hole 114e and a passage 15d. The pressure-switching
mechanism 21 switches to enable or disable the introduction of discharge pressure.
The cylinder chamber 14d communicates with the suction chamber 16 through the pressure-releasing
hole 114f, a passage 15f, an expansion mechanism 15fa, and the passage 15c. The cylinder
chamber 14c communicates with the suction chamber 16 through the pressure-releasing
hole 114c, a passage 15e, an expansion mechanism 15ea, and the passage 15c.
[0070] The pressure-switching mechanism 31 has the same configuration as the pressure-switching
mechanism 21. If the first figure "2" in each of the reference numerals given to the
respective elements of the pressure-switching mechanism 21 is changed to "3", a reference
numeral denoting a corresponding one of the elements of the pressure-switching mechanism
31 is obtained. The pressure-switching mechanism 31 switches whether to enable or
disable the introduction of discharge pressure into the cylinder chamber 14d.
[0071] Table 1 below summarizes the open/closed states of the solenoid valve 27 and a solenoid
valve 37 for Vi values at individual levels of high, moderate, and low in Embodiment
3. The table is to be referred to in the following description of relevant operations.
[Table 1]
|
Solenoid valve 27 |
Solenoid valve 37 |
High Vi value |
Closed |
Closed |
Moderate Vii value |
Closed |
Open |
Low Vi value |
Open |
Closed |
(1) Operation with High Vi Value
[0072] Fig. 8 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 3 of the present
invention that operate at a high internal volume ratio.
[0073] When the Vi value is high, as summarized in Table 1, the solenoid valve 27 is closed,
and the solenoid valve 37 is closed. Since the solenoid valve 27 is closed, suction
pressure is introduced from the pressure-switching mechanism 21 into the cylinder
chamber 14c. Furthermore, since the solenoid valve 37 is closed, suction pressure
is introduced into the cylinder chamber 14d. That is, the cylinder chamber 14c and
the cylinder chamber 14d are both under suction pressure. That is, the cylinder chamber
14b is under suction pressure. Furthermore, discharge pressure is constantly introduced
into the cylinder chamber 14a.
[0074] As described above, with respect to the Vi piston 13 as a partition, discharge pressure
is introduced into the cylinder chamber 14a, whereas suction pressure is introduced
into the cylinder chamber 14b. Therefore, the operation with a high Vi value according
to Embodiment 1 also applies here. Specifically, the variable Vi valve 9 moves leftward
as indicated by the arrow illustrated in the drawing. That is, the driving device
11 causes the variable Vi valve 9 to move leftward as indicated by the arrow illustrated
in the drawing. Thus, the timing of opening the discharge port 8 is slowed.
(2) Operation with Moderate Vi Value
[0075] Fig. 9 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 3 of the present
invention that operate at a moderate internal volume ratio.
[0076] When the Vi value is moderate, the solenoid valve 27 is closed, whereas the solenoid
valve 37 is open. Since the solenoid valve 27 is closed, suction pressure is introduced
into the cylinder chamber 14d. Furthermore, since the solenoid valve 37 is open, discharge
pressure is introduced into the cylinder chamber 14d. Furthermore, discharge pressure
is constantly introduced into the cylinder chamber 14a. Consequently, the cylinder
chamber 14a and the cylinder chamber 14d are under discharge pressures of the same
level, whereas the cylinder chamber 14c is under suction pressure.
[0077] Note that the cylinder chamber 14d is under suction pressure both in the case of
a high Vi value and in a case of a low Vi value to be described below. Therefore,
when the Vi value is switched from the high or low level to the moderate level, the
pressure in the cylinder chamber 14d changes from suction pressure to discharge pressure
because the state of the solenoid valve 37 is switched from closed to open.
[0078] More specifically, when the Vi value is switched from the high level to the moderate
level, the pressure in the cylinder chamber 14d in which the Vi piston 39 is positioned
as illustrated in Fig. 8 is raised from suction pressure to discharge pressure. Accordingly,
the Vi piston 39 moves rightward together with the interlocked piston 40. With the
rightward movement of the Vi piston 39, the variable Vi valve 9 is pushed by the interlocked
piston 40 to move rightward. Then, when the Vi piston 39 stops moving by coming into
contact with the positioning wall 42, the Vi piston 13 and the variable Vi valve 9
stop moving correspondingly and are positioned as illustrated in Fig. 9.
[0079] When the Vi value is switched from the low level to the moderate level, the pressure
in the cylinder chamber 14d in which the Vi piston 39 is positioned as illustrated
in Fig. 10 to be referred to below is raised from suction pressure to discharge pressure.
Meanwhile, since the solenoid valve 27 is closed, the cylinder chamber 14c comes to
receive suction pressure. Such a pressure difference between the cylinder chamber
14d and the cylinder chamber 14c causes the Vi piston 39 to move rightward and stop
moving by coming into contact with the positioning wall 42.
[0080] When the Vi value is low as to be described below, the cylinder chamber 14a and
the cylinder chamber 14c are under discharge pressure. When the Vi value is switched
to a moderate level and the solenoid valve 27 is therefore closed, the pressure in
the cylinder chamber 14c changes from discharge pressure to suction pressure. Such
a pressure difference between the cylinder chamber 14a and the cylinder chamber 14c
causes the Vi piston 13 to move leftward from the position illustrated in Fig. 10
and stop moving by coming into contact with the interlocked piston 40. Thus, the Vi
piston 13 is positioned as illustrated in Fig. 9.
[0081] As described above, when the Vi value is moderate, the Vi piston 13 is stopped by
coming into contact with the interlocked piston 40, with the Vi piston 39 being in
contact with the positioning wall 42. In this state, the variable Vi valve 9 is positioned
more rightward than in the case of a high Vi value illustrated in Fig. 8. Consequently,
the timing of opening the discharge port 8 is advanced from the timing in the case
of a high Vi value.
(3) Operation with Low Vi Value
[0082] Fig. 10 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 3 of the present
invention that operate at a low internal volume ratio.
[0083] When the Vi value is low, the solenoid valve 27 is open. Therefore, discharge pressure
is introduced from the pressure-switching mechanism 21 into the cylinder chamber 14c.
Whereas, the solenoid valve 37 is closed. Therefore, suction pressure is introduced
into the cylinder chamber 14d. Furthermore, discharge pressure is constantly introduced
into the cylinder chamber 14a. Consequently, the cylinder chamber 14a and the cylinder
chamber 14c are under discharge pressure, whereas the cylinder chamber 14d is under
suction pressure. Hence, there is no pressure difference between the front and rear
surfaces of the Vi piston 13 that are defined in the moving direction in the cylinder
12.
[0084] Regarding two ends, defined in the moving direction, of the variable Vi valve 9
coupled to the Vi piston 13, the suction-side end 9g of the valve body 9a is under
suction pressure, and the driving-device-side end 9h of the guide portion 9b is under
discharge pressure, as with the case of Embodiment 1. Furthermore, the discharge-port-side
end 9d of the valve body 9a is under discharge pressure obtained immediately after
the discharge, and the discharge-port-side end 9e of the guide portion 9b is under
discharge pressure that is equal to but acts in the opposite direction to the pressure
acting on the discharge-port-side end 9d. Hence, loads applied to the discharge-port-side
end 9d and the discharge-port-side end 9e cancel each other out. Consequently, the
variable Vi valve 9 moves rightward in the drawing because of the difference between
the pressures acting on the driving-device-side end 9h and the suction-side end 9g.
The variable Vi valve 9 stops at a position where the suction-side end 9g thereof
comes into contact with the wall of the casing 2. Therefore, the variable Vi valve
9 is accurately positioned for the low Vi value. Thus, the timing of opening the discharge
port 8 is advanced from the timing in the case of a moderate Vi value.
[0085] According to Embodiment 3, the Vi value is controllable among three levels with two
pressure-switching mechanisms each including a single solenoid valve. Consequently,
a screw compressor that is inexpensive and has a simple configuration can be obtained.
Embodiment 4
[0086] Embodiment 4 of the present invention is different from Embodiment 3 in that the
pressure-switching mechanism 21 is connected to the cylinder chamber 14a instead of
the cylinder chamber 14c. More specifically, the pressure-switching mechanism 21 is
connected to the pressure-introducing hole 114a, and the pressure-introducing hole
114b is made to communicate with the suction chamber 16.
[0087] Now, an operation of the variable Vi valve 9 according to Embodiment 4 will be described.
As with the case of Embodiment 3, the Vi value is settable among three levels of high,
moderate, and low.
[0088] Table 2 below summarizes the open/closed states of the solenoid valve 27 and the
solenoid valve 37 for the Vi values at individual levels of high, moderate, and low
in Embodiment 4. The table is to be referred to in the following description of relevant
operations.
[Table 2]
|
Solenoid valve 27 |
Solenoid valve 37 |
High Vi value |
Open |
Closed |
Moderate Vii value |
Open |
Open |
Low Vi value |
Closed |
Closed |
(1) Operation with High Vi Value
[0089] Fig. 11 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 4 of the present
invention that operate at a high internal volume ratio.
[0090] When the Vi value is high, the solenoid valve 27 is open, whereas the solenoid valve
37 is closed. Since the solenoid valve 27 is open, discharge pressure is introduced
from the pressure-switching mechanism 21 into the cylinder chamber 14a. Furthermore,
since the solenoid valve 37 is closed, suction pressure is introduced into the cylinder
chamber 14d. Furthermore, pressure is constantly introduced into the cylinder chamber
14c.
[0091] As described above, with respect to the Vi piston 13 as a partition, discharge pressure
is introduced into the cylinder chamber 14a, whereas suction pressure is introduced
into the cylinder chamber 14b. Therefore, the operation with a high Vi value according
to Embodiment 1 also applies here. Specifically, the variable Vi valve 9 moves leftward
as indicated by the arrow illustrated in the drawing. That is, the driving device
11 causes the variable Vi valve 9 to move leftward as indicated by the arrow illustrated
in the drawing. Thus, the timing of opening the discharge port 8 is slowed.
(2) Operation with Moderate Vi Value
[0092] Fig. 12 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 4 of the present
invention that operate at a moderate internal volume ratio.
[0093] When the Vi value is moderate, the solenoid valve 27 is open, and the solenoid valve
37 is open. Since the solenoid valve 27 is open, discharge pressure is introduced
into the cylinder chamber 14a. Furthermore, since the solenoid valve 37 is open, discharge
pressure is introduced into the cylinder chamber 14d. Furthermore, suction pressure
is constantly introduced into the cylinder chamber 14b. Consequently, the cylinder
chamber 14a and the cylinder chamber 14d are under discharge pressures of the same
level, whereas the cylinder chamber 14c is under suction pressure.
[0094] When the Vi value is switched from the high level to the moderate level, the pressure
in the cylinder chamber 14d in which the Vi piston 39 is positioned illustrated in
Fig. 11 is raised from suction pressure to discharge pressure. Accordingly, the Vi
piston 39 moves rightward together with the interlocked piston 40. With the rightward
movement of the Vi piston 39, the variable Vi valve 9 is pushed by the interlocked
piston 40 to move rightward. Then, when the Vi piston 39 stops moving by coming into
contact with the positioning wall 42, the Vi piston 13 and the variable Vi valve 9
stop moving correspondingly and are positioned as illustrated in Fig. 12.
[0095] When the Vi value is switched from the low level to the moderate level, the pressure
in the cylinder chamber 14d in which the Vi piston 39 is positioned as illustrated
in Fig. 13 to be referred to below is raised from suction pressure to discharge pressure.
Meanwhile, the cylinder chamber 14c is constantly under suction pressure. Such a pressure
difference between the cylinder chamber 14d and the cylinder chamber 14c causes the
Vi piston 39 to move rightward and stop moving by coming into contact with the positioning
wall 42. In addition, when the Vi value is low as to be described below, the cylinder
chamber 14a and the cylinder chamber 14c are both under suction pressure. However,
when the Vi value is switched to the moderate level, the solenoid valve 27 is closed.
Consequently, the pressure in the cylinder chamber 14a changes from suction pressure
to discharge pressure. Such a pressure difference between the cylinder chamber 14a
and the cylinder chamber 14c causes the Vi piston 13 to move leftward from the position
illustrated in Fig. 13 and stop moving by coming into contact with the interlocked
piston 40. Thus, the Vi piston 13 is positioned as illustrated in Fig. 12.
[0096] As described above, when the Vi value is moderate, the Vi piston 13 stops by coming
into contact with the interlocked piston 40, with the Vi piston 39 being in contact
with the positioning wall 42. In this state, the variable Vi valve 9 is positioned
more rightward than in the case of a high Vi value illustrated in Fig. 11. Consequently,
the timing of opening the discharge port 8 is advanced from the timing in the case
of a high Vi value.
(3) Operation with Low Vi Value
[0097] Fig. 13 is a schematic diagram illustrating the driving device and the pressure-switching
mechanisms included in the screw compressor according to Embodiment 4 of the present
invention that operate at a low internal volume ratio.
[0098] When the Vi value is low, the solenoid valve 27 is closed. Therefore, suction pressure
is introduced from the pressure-switching mechanism 21 into the cylinder chamber 14a.
Furthermore, the solenoid valve 37 is closed. Therefore, discharge pressure is introduced
into the cylinder chamber 14d. Furthermore, suction pressure is constantly introduced
into the cylinder chamber 14c. That is, the cylinder chamber 14a, the cylinder chamber
14c, and the cylinder chamber 14d are under suction pressure. Hence, there is no pressure
difference between the front and rear surfaces of the Vi piston 13 that are defined
in the moving direction in the cylinder 12.
[0099] Regarding two ends, defined in the moving direction, of the variable Vi valve 9 coupled
to the Vi piston 13, the suction-side end 9g of the valve body 9a is under suction
pressure, and the driving-device-side end 9h of the guide portion 9b is under discharge
pressure, as with the case of Embodiment 1. Furthermore, the discharge-port-side end
9d of the valve body 9a is under discharge pressure obtained immediately after the
discharge, and the discharge-port-side end 9e of the guide portion 9b is under discharge
pressure that is equal to but acts in the opposite direction to the pressure acting
on the discharge-port-side end 9d. Hence, loads applied to the discharge-port-side
end 9d and the discharge-port-side end 9e cancel each other out. Consequently, the
variable Vi valve 9 moves rightward in the drawing because of the difference between
the pressures acting on the driving-device-side end 9h and the suction-side end 9g.
The variable Vi valve 9 stops at a position where the suction-side end 9g thereof
comes into contact with the wall of the casing 2. Therefore, the variable Vi valve
9 is accurately positioned for the low Vi value. Thus, the timing of opening the discharge
port 8 is advanced from the timing in the case of a moderate Vi value.
[0100] Embodiment 4 is different from Embodiment 3 in that the pressure-switching mechanism
21 is connected to the cylinder chamber 14a instead of the cylinder chamber 14c, and
can produce the same advantageous effects as Embodiment 3.
Embodiment 5
[0101] Embodiment 5 of the present invention concerns a pressure-switching mechanism having
a simpler configuration.
[0102] Fig. 14 is a schematic diagram of a screw compressor according to Embodiment 5 of
the present invention.
[0103] A screw compressor 1 according to Embodiment 5 includes a pressure-switching mechanism
21A instead of the pressure-switching mechanism 21 employed in Embodiment 1. The pressure-switching
mechanism 21A includes a solenoid valve 27 that switches whether to enable or disable
the introduction of discharge pressure from the discharge chamber 7 into the cylinder
chamber 14b by opening or closing the passage 30 through which the discharge chamber
7 and the cylinder chamber 14b communicate with each other. In other words, the pressure-switching
mechanism 21A is obtained by removing the switching piston 23, the rod 24, and the
spring 25 from the pressure-switching mechanism 21 according to Embodiment 1. The
pressure-switching mechanism 21A corresponds to the second mechanism according to
the present invention.
[0104] When the Vi value is high, the solenoid valve 27 is closed. Accordingly, discharge
pressure is not introduced into the cylinder chamber 14b. Moreover, the pressure in
the cylinder chamber 14b is released from the pressure-releasing hole 114c and is
eventually reduced to suction pressure. Thus, the same pressure state as illustrated
in Fig. 3 is established in the cylinder 12, and the same operation as illustrated
in Fig. 3 is realized.
[0105] When the Vi value is low, the solenoid valve 27 is open. Accordingly, discharge pressure
is introduced into the cylinder chamber 14b. Thus, the same pressure state as illustrated
in Fig. 4 is established, and the same operation as illustrated in Fig. 4 is realized.
[0106] According to Embodiment 5 described above, a much simpler configuration is realized
by removing the switching piston 23, the rod 24, and the spring 25 from the mechanism
according to Embodiment 1. Consequently, a screw compressor that is inexpensive and
has a simple configuration can be obtained.
Embodiment 6
[0107] Embodiment 6 of the present invention is obtained by simplifying Embodiment 2 and
is also regarded as a combination of Embodiment 2 and Embodiment 5.
[0108] Fig. 15 is a schematic diagram of a screw compressor according to Embodiment 6 of
the present invention.
[0109] Embodiment 6 is obtained by applying the pressure-switching mechanism 21 according
to Embodiment 2 illustrated in Fig. 7 to the pressure-switching mechanism 21A according
to Embodiment 5 illustrated in Fig. 14.
[0110] Such a configuration is much simpler than the configuration according to Embodiment
2. Consequently, a screw compressor that is inexpensive and has a simple configuration
can be obtained.
[0111] The mechanism of opening and closing each of the solenoid valves 27 and 37 is the
same as in Embodiment 2.
[0112] While Embodiment 6 concerns a configuration in which the pressure-switching mechanism
21 is simplified, a configuration in which the pressure-switching mechanism 31 is
simplified or a configuration in which both the pressure-switching mechanism 21 and
the pressure-switching mechanism 31 are simplified is also acceptable.
[0113] While Embodiments 1 to 6 each concern a case where one variable Vi valve 9 is provided
for one driving device 11, two variable Vi valves 9 may alternatively be provided.
That is, the number of variable Vi valves 9 is not limited. Moreover, the pressures
to be introduced into the cylinder chambers 14a, 14b, 26a, and 26b are not limited
to discharge pressure and suction pressure. For example, intermediate pressure may
also be introduced. Intermediate pressure is a pressure that is lower than the discharge
pressure but higher than the suction pressure.
[0114] Furthermore, the refrigerant to be used in the screw compressor 1 is not limited
to a particular refrigerant and may be, for example, selected from any of those having
low GWPs, standing for global warming potentials, with consideration for factors affecting
the environment. Examples of the refrigerant having a low GWP include R32, HFO-1123,
HFO-1234yf, or a mixed refrigerant containing at least one of the foregoing refrigerants.
The refrigerant to be used in the screw compressor 1 may alternatively be a natural
refrigerant such as carbon dioxide.
Reference Signs List
[0115] 1 screw compressor 2 casing 3 motor 3a stator 3b motor rotor 4 screw shaft 5 screw
rotor 5a screw groove 6 compression chamber 7 discharge chamber 8 discharge port 9
variable Vi valve 9a valve body 9b guide portion 9c coupling portion 9d discharge-port-side
end 9e discharge-port-side end 9f discharge air gap 9g suction-side end 9h driving-device-side
end 10 rod 11 driving device 12 cylinder 13 Vi piston 14 cylinder 14a cylinder chamber
14b cylinder chamber 14c cylinder chamber 14d cylinder chamber 15a passage 15b passage
15c passage 15ca expansion mechanism 15d passage 15f passage 15fa expansion mechanism
15e passage 15ea expansion mechanism 16 suction chamber 21 pressure-switching mechanism
21A pressure-switching mechanism 22 cylinder 23 switching piston 24 rod 25 spring
26a cylinder chamber 26b cylinder chamber 27 solenoid valve 28 passage 28a passage
28b passage 28ba expansion mechanism 28c passage 28d passage 30 passage 31 pressure-switching
mechanism 37 solenoid valve 39 Vi piston 40 interlocked piston 41 coupling portion
42 positioning wall 42a hole 50 controller 114a pressure-introducing hole 114b pressure-introducing
hole 114c pressure-releasing hole 114e pressure-introducing hole 114f pressure-releasing
hole 214a pressure-introducing hole 214b pressure-releasing hole 214c pressure-releasing
hole 214d pressure-introducing hole
1. A screw compressor comprising:
a casing in which a discharge chamber and a suction chamber are provided;
a screw rotor, on an outer peripheral surface of which a plurality of grooves forming
a compression chamber are provided, the screw rotor being rotatable in the casing;
a variable Vi valve movable in an axial direction of the screw rotor and whose stopping
position is shifted to change an internal volume ratio that is a ratio between a volume
of the compression chamber at completion of suction and a volume of the compression
chamber at completion of discharge;
a driving device including a Vi piston coupled to the variable Vi valve, and a driving
cylinder that houses the Vi piston movably in the driving cylinder; and
a pressure-switching mechanism that switches pressure to be introduced into the driving
device,
wherein an inside of the driving cylinder is divided by the Vi piston into two cylinder
chambers,
wherein the driving device moves the Vi piston by changing pressure in one of the
two cylinder chambers to control a position of the variable Vi valve,
wherein the pressure-switching mechanism includes a solenoid valve configured to open
to form a first passage through which the discharge chamber and the one cylinder chamber
communicate with each other, and close to block the first passage, the solenoid valve
being switched to open to enable introduction of discharge pressure from the discharge
chamber into the one cylinder chamber or close to disable introduction of discharge
pressure from the discharge chamber into the one cylinder chamber; a switching cylinder
communicating with the first passage extending between the solenoid valve and the
one cylinder chamber; a switching piston movably housed in the switching cylinder;
and a spring that is compressed with a movement of the switching piston,
wherein an inside of the switching cylinder is divided by the switching piston into
a first switching cylinder chamber into which suction pressure is constantly introduced
and in which the spring is provided, and a second switching cylinder chamber that
communicates with the first passage,
wherein a second passage through which the first switching cylinder chamber and the
one cylinder chamber communicate with each other is opened or closed depending on
a position of the switching piston that receives a spring force exerted by the spring,
and
wherein the pressure in the one cylinder chamber changes when the first passage is
opened or closed with opening or closing of the solenoid valve while the second passage
is opened or closed with the movement of the switching piston.
2. The screw compressor of claim 1, wherein the second passage is provided with a first
expansion mechanism.
3. A screw compressor comprising:
a casing in which a discharge chamber and a suction chamber are provided;
a screw rotor, on an outer peripheral surface of which a plurality of grooves forming
a compression chamber are provided, the screw rotor being rotatable in the casing;
a variable Vi valve movable in an axial direction of the screw rotor and whose stopping
position is shifted to change an internal volume ratio that is a ratio between a volume
of the compression chamber at completion of suction and a volume of the compression
chamber at completion of discharge;
a driving device including a Vi piston coupled to the variable Vi valve, and a driving
cylinder that houses the Vi piston movably in the driving cylinder; and
a pressure-switching mechanism that switches pressure to be introduced into the driving
device,
wherein an inside of the driving cylinder is divided by the Vi piston into two cylinder
chambers,
wherein the driving device moves the Vi piston by changing pressure in one of the
two cylinder chambers to control a position of the variable Vi valve, and
wherein the pressure-switching mechanism includes a solenoid valve configured to open
to form a first passage through which the discharge chamber and the one cylinder chamber
communicate with each other, and close to block the first passage, the solenoid valve
being switched to open to enable introduction of discharge pressure from the discharge
chamber into the one cylinder chamber or close to disable introduction of discharge
pressure from the discharge chamber into the one cylinder chamber, and wherein the
pressure in the one cylinder chamber changes with opening or closing of the solenoid
valve.
4. The screw compressor of any one of claims 1 to 3,
wherein the two cylinder chambers are a first cylinder chamber and a second cylinder
chamber in order of arrangement from a side nearer to the variable Vi valve,
wherein discharge pressure is constantly introduced into the first cylinder chamber,
and
wherein the second cylinder chamber corresponds to the one cylinder chamber and communicates
with the suction chamber through a second expansion mechanism, and the pressure in
the second cylinder chamber is switched between discharge pressure and suction pressure
depending on whether the solenoid valve is opened or closed.
5. The screw compressor of any one of claims 1 to 3,
wherein the two cylinder chambers are a first cylinder chamber and a second cylinder
chamber in order of arrangement from a side nearer to the variable Vi valve,
wherein the first cylinder chamber corresponds to the one cylinder chamber and communicates
with the suction chamber through a second expansion mechanism, and the pressure in
the first cylinder chamber is switched between discharge pressure and suction pressure
depending on whether the solenoid valve is opened or closed, and
wherein suction pressure is constantly introduced into the second cylinder chamber.
6. A screw compressor comprising:
a casing in which a discharge chamber and a suction chamber are provided;
a screw rotor, on an outer peripheral surface of which a plurality of grooves forming
a compression chamber are provided, the screw rotor being rotatable in the casing;
a variable Vi valve movable in an axial direction of the screw rotor and whose stopping
position is shifted to change an internal volume ratio that is a ratio between a volume
of the compression chamber at completion of suction and a volume of the compression
chamber at completion of discharge;
a driving device including a first Vi piston coupled to the variable Vi valve, and
a driving cylinder that houses the first Vi piston movably in the driving cylinder;
and
two pressure-switching mechanisms that each switch pressure to be introduced into
the driving device,
wherein the driving device includes
a second Vi piston that operates independently of the first Vi piston;
an interlocked piston provided between the first Vi piston and the second Vi piston
and coupled to the second Vi piston through a coupling portion; and
a positioning wall provided between the second Vi piston and the interlocked piston
and having a hole through which the coupling portion movably extends,
wherein an inside of the driving cylinder is divided by the first Vi piston and the
second Vi piston into three cylinder chambers,
wherein the driving device controls
a position of the variable Vi valve to move the second Vi piston between a position
where the second Vi piston comes into contact with the positioning wall and a position
where the second Vi piston is out of contact with the positioning wall by changing
pressure in at least one of the three cylinder chambers, and while controlling the
first Vi piston to move together with the second Vi piston or independently of the
second Vi piston;
wherein each of the two pressure-switching mechanisms is provided for corresponding
one of two of the three cylinder chambers;
wherein the two pressure-switching mechanisms are first mechanisms or second mechanisms,
or one of the two pressure-switching mechanisms is the first mechanism while an other
is the second mechanism,
wherein the first mechanism includes
a solenoid valve configured to open to form a first passage through which the discharge
chamber and the one cylinder chamber communicate with each other, and close to block
the first passage, the solenoid valve being switched to open to enable introduction
of discharge pressure from the discharge chamber into the one cylinder chamber or
close to disable introduction of discharge pressure from the discharge chamber into
the one cylinder chamber; a switching cylinder communicating with the first passage
extending between the solenoid valve and the one cylinder chamber; a switching piston
movably housed in the switching cylinder; and a spring that is compressed with a movement
of the switching piston,
wherein an inside of the switching cylinder is divided by the switching piston into
a first switching cylinder chamber into which suction pressure is constantly introduced
and in which the spring is provided, and a second switching cylinder chamber that
communicates with the first passage,
wherein a second passage through which the first switching cylinder chamber and the
one cylinder chamber communicate with each other is allowed to communicate or not
communicate depending on a position of the switching piston that receives a spring
force exerted by the spring,
wherein the pressure in the one cylinder chamber changes when the first passage is
opened or closed with opening or closing of the solenoid valve while the second passage
is opened or closed with the movement of the switching piston, and
wherein the second mechanism includes
a solenoid valve configured to open to form the first passage, and close to block
the first passage, the solenoid valve being switched to open to enable introduction
of discharge pressure from the discharge chamber into the one cylinder chamber or
close to disable introduction of discharge pressure from the discharge chamber into
the one cylinder chamber, and the pressure in the one cylinder chamber changes with
opening or closing of the solenoid valve.
7. The screw compressor of claim 6,
wherein the three cylinder chambers are a first cylinder chamber, a second cylinder
chamber, and a third cylinder chamber in order of arrangement from a side nearer to
the variable Vi valve,
wherein discharge pressure is constantly introduced into the first cylinder chamber,
and
wherein the second cylinder chamber and the third cylinder chamber correspond to the
two cylinder chambers, respectively, and each communicate with the suction chamber
through an expansion mechanism; and pressure in each of the second cylinder chamber
and the third cylinder chamber is switched between discharge pressure and suction
pressure depending on whether the solenoid valves are opened or closed individually.
8. The screw compressor of claim 6,
wherein the three cylinder chambers are a first cylinder chamber, a second cylinder
chamber, and a third cylinder chamber in order of arrangement from a side nearer to
the variable Vi valve,
wherein the first cylinder chamber and the third cylinder chamber correspond to the
two cylinder chambers, respectively, and each communicate with the suction chamber
through an expansion mechanism; and pressure in each of the first cylinder chamber
and the third cylinder chamber is switched between discharge pressure and suction
pressure depending on whether the solenoid valves are opened or closed individually,
and
wherein suction pressure is constantly introduced into the second cylinder chamber.