CN102395759A - Fluid machine and refrigeration cycle apparatus - Google Patents

Abstract

The invention provides a fluid machine and a refrigeration cycle device. The fluid machine (8A) includes: an expander (4) having an expander suction hole (4a) and an expander discharge hole (4b); a compressor having a compressor suction hole (6a) and a compressor discharge hole (6b) machine (6); and the shaft (81) connecting the expander (4) and the compressor (6). The expander suction hole (4a) and the compressor suction hole (4a) open and close as the shaft (81) rotates. The fluid machine is maintained such that the expander suction hole (4a) is open while the compressor suction hole (6a) is closed, and the compressor suction hole (6a) is closed while the expander suction hole (4a) is closed. ) is in an open state and does not communicate with the compressor discharge hole (6b).

Description

Fluid Machinery and Refrigeration Cycle Devices

technical field

The present invention relates to a fluid machine used in a water heater, an air conditioner, and the like, and a refrigeration cycle device using the fluid machine.

Background technique

Conventionally, there is known a fluid machine in which an expander and a compressor are connected via a shaft, and the compressor is driven by power recovered from a working fluid expanded in the expander. For example, Patent Document 1 discloses a fluid machine 100 as shown in FIG. 12 .

As shown in FIG. 12 , in a fluid machine 100 , an expander 110 and a compressor 120 are connected via a shaft 101 . Both the expander 110 and the compressor 120 are of a rotary type, and the shaft 101 has a first eccentric portion 102 for the expander 110 and a second eccentric portion 103 for the compressor 120 .

As shown in FIG. 13 , the expander 110 has an expander piston 112 fitted to the first eccentric portion 102 of the shaft 101 , and an expander cylinder 111 that accommodates the expander piston 112 . Furthermore, a crescent-shaped expander working chamber 113 is formed between the inner peripheral surface of the expander cylinder 111 and the outer peripheral surface of the expander piston 112 . The expander working chamber 113 is divided into a suction side and a discharge side by an expander partition member 114 . The expander partition member 114 is integrally formed with the expander piston 112 , and a columnar shoe 117 that supports the expander partition member 114 reciprocally is rotatable on the expander cylinder 111 . That is, the expander piston 112 swings with the center of the shoe 117 as a fulcrum while changing the distance from the fulcrum.

The expander cylinder 111 is provided with a suction hole 110 a for introducing working fluid into the expander working chamber 113 and a discharge hole 110 b for discharging the working fluid from the expander working chamber 113 . The suction hole 110 a communicates with the expander working chamber 113 through a communication hole 115 formed in the shoe 117 and a communication groove 116 formed in the expander partition member 113 at a predetermined timing. That is, the shoe 117 and the expander partition member 113 constitute a suction control mechanism that opens and closes the suction hole 110 a as the shaft 101 rotates. The timing at which the suction hole 110 a is opened (communicated with the expander working chamber 113 ) is from when the expander piston 112 is located at the top dead center at which the expander partition member 114 is retracted most until it rotates by about 140°.

As shown in FIG. 14 , the compressor 120 has a compressor piston 122 formed of a roller bearing and fitted to the second eccentric portion 103 of the shaft 101 , and a compressor cylinder 121 that accommodates the compressor piston 122 . Furthermore, a crescent-shaped compressor working chamber 123 is formed between the inner peripheral surface of the compressor cylinder 121 and the outer peripheral surface of the compressor piston 122 . The compressor working chamber 123 is partitioned into a suction side and a discharge side by a compressor partition member 124 . The compressor separation member 124 is spring pressed onto the compressor piston 122 .

The compressor working cylinder 121 is provided with a suction hole 120a for introducing the working fluid to the compressor working chamber 123, and the blocking member adjacent to the compressor working cylinder 121 and the compressor piston 122 is provided with a suction hole 120a for discharging the working fluid from the compressor working chamber 113. The discharge hole 120b for the working fluid. The suction hole 120a opens on the inner peripheral surface of the compressor cylinder 121, and is closed by the compressor piston 122 only while the sliding point of the compressor piston 122 sliding on the inner peripheral surface of the compressor cylinder 121 is located on the suction hole 120a. closure.

In addition, Patent Document 1 discloses a refrigeration cycle device 200 shown in FIG. 15 manufactured using the fluid machine 100 described above. This refrigeration cycle device 200 is a device that uses the compressor 120 of the fluid machine 100 to pre-boost the working fluid sucked into the main compressor 210. The main compressor 210, radiator 220, expander 110, evaporator 230 and compressor Machines 120 are connected in sequence through flow paths to form a working fluid circuit.

【Prior technical literature】

【Patent Literature】

[Patent Document 1] Japanese Patent Laid-Open No. 2004-324595

Assume that the fluid machine 100 is self-starting under the pressure of the working fluid in the refrigeration cycle device 200 as shown in FIG. 15 without having a driving mechanism such as a motor. That is, by starting the main compressor 210 , the high-pressure working fluid flows into the suction side of the expander working chamber 113 of the expander 110 . As a result, a differential pressure is generated between the suction side and the discharge side of the expander working chamber 113 , and torque is applied to the shaft 101 by the differential pressure to start the fluid machine 100 .

However, when the fluid machine 100 stops with the suction hole 110 a of the expander 110 closed, high-pressure working fluid cannot flow into the expander working chamber 113 , and no torque for rotating the shaft 101 is generated.

In view of this, the inventors of the present invention considered that the high-pressure working fluid discharged from the main compressor is also guided to the compressor of the fluid machine at the time of start-up before the present invention, so that the compressor also imparts rotation to the shaft. moment. That is, a bypass passage connecting the high-pressure flow path between the main compressor and the radiator or the radiator and the expander and the low-pressure flow path between the evaporator and the compressor is provided, and the high-pressure working fluid is also sent to the compressor when starting. The suction side of the compressor working chamber flows in, whereby a differential pressure is also generated between the suction side and the discharge side of the compressor working chamber. Accordingly, torque can be applied to the shaft also in the compressor.

However, even if the above-mentioned technology is applied to the fluid machine 100 disclosed in Patent Document 1, there are cases where no torque to rotate the shaft 101 is generated. The reason for this is as follows.

In the fluid machine 100 disclosed in Patent Document 1, the position of the expander partition member 114 coincides with the position of the compressor partition member 124 in the axial direction of the shaft 101, and the eccentric direction of the first eccentric portion 102 is the same as that of the second eccentric portion 103. The eccentric directions are staggered by 180°. In addition, in the compressor 120 , while the sliding point of the compressor piston 121 approaches the suction hole 120 a through the discharge hole 120 b , the suction hole 120 a communicates with the discharge hole 120 b via the compressor working chamber 123 .

Therefore, assuming that the rotation angle of the shaft 101 when the expander piston 112 is at the top dead center is 0°, in the expander 110, the working fluid can flow to The suction side of the expander working chamber 113 flows in. On the other hand, in the compressor 120, the suction hole 120a of the compressor 120 is closed by the compressor piston 122 while the rotation angle of the shaft 101 is about 190° to about 200°, but during other periods, The working fluid can flow into the suction side of the compressor working chamber 123 .

However, when the rotation angle of the shaft 101 is about 190° to about 200°, both the expander suction hole 110a and the compressor suction hole 120a are closed, and neither the expander 110 nor the compressor 120 can generate The torque at which shaft 110 rotates. In addition, when the rotation angle of the shaft 101 is from about 180° at which the sliding point of the compressor piston 121 passes through the discharge hole 120b to about 190° at which the sliding point of the compressor piston 121 is adjacent to the suction hole 120a, as described above, the suction hole 120a communicates with the discharge hole 120b via the compressor working chamber 123, and the working fluid flowing into the compressor working chamber 123 from the suction hole 120a is discharged from the discharge hole 120b. In addition, at this time, the suction hole 110a of the expander 110 is also closed. Therefore, when the fluid machine 100 stops when the shaft rotation angle is between about 180° and about 200°, at this time, the pressure of the working fluid cannot be used to generate torque to rotate the shaft 101, and the fluid machine 100 cannot be self-started. .

Contents of the invention

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a fluid machine that can be self-started by the pressure of a working fluid regardless of the state of stop, and a refrigeration cycle device using the fluid machine.

In order to solve the above-mentioned problems, the fluid machine provided by the present invention includes: an expander that expands the working fluid sucked in from the expander suction hole and discharges it from the expander discharge hole, thereby recovering power from the working fluid; the working fluid sucked in from the compressor suction hole is pressurized and discharged from the compressor discharge hole; a shaft that connects the expander and the compressor so that the compressor is driven by the power recovered by the expander, The expander suction hole and the compressor suction hole open and close as the shaft rotates, and the fluid machine maintains the expander suction hole open while the compressor suction hole is closed. During the period when the expander suction hole is closed, the compressor suction hole is in an open state and does not communicate with the compressor discharge hole.

In addition, the refrigerating cycle device provided by the present invention uses the above-mentioned fluid machine, and includes: a working fluid circuit that circulates the working fluid, including a main compressor that compresses the working fluid, a radiator that dissipates heat from the compressed working fluid, The expander expands the working fluid flowing out of the radiator, the evaporator evaporates the expanded working fluid, and the working fluid flowing out of the evaporator is pressurized and supplied to the main compressor. the compressor; a bypass passage that connects a portion between the main compressor and the radiator or a portion between the radiator and the expander, and the evaporator in the working fluid circuit part of the connection between the machine and the compressor.

【Invention effect】

According to the above structure, the working fluid can always flow into one or both of the suction side of the expander working chamber and the suction side of the compressor working chamber, and the working fluid flowing into the compressor working chamber is prevented from being discharged from the compressor discharge hole. Therefore, regardless of the state in which the fluid machine stops, the pressure of the working fluid can be used to self-start the fluid machine.

Description of drawings

FIG. 1 is a configuration diagram of a refrigeration cycle apparatus using a fluid machine according to a first embodiment of the present invention.

Fig. 2 is a longitudinal sectional view of the fluid machine according to the first embodiment of the present invention.

Fig. 3 is a sectional view taken along line III-III of Fig. 2 .

Fig. 4 is a sectional view taken along line IV-IV of Fig. 2 .

Fig. 5 is a sectional view taken along line V-V of Fig. 2 .

6A to 6C are schematic views of the operation of the fluid machine according to the first embodiment of the present invention.

7A to 7C are schematic diagrams of the operation of the fluid machine according to the first embodiment of the present invention.

Fig. 8 is a longitudinal sectional view of a fluid machine according to a second embodiment of the present invention.

Fig. 9 is a sectional view taken along line IX-IX of Fig. 8 .

10A to 10C are schematic views of the operation of the fluid machine according to the second embodiment of the present invention.

11A to 11C are schematic views of the operation of the fluid machine according to the second embodiment of the present invention.

Fig. 12 is a longitudinal sectional view of a conventional fluid machine.

Fig. 13 is a sectional view taken along line A-A of Fig. 12 .

Fig. 14 is a sectional view taken along line B-B of Fig. 12 .

Fig. 15 is a configuration diagram of a refrigeration cycle using the fluid machine shown in Fig. 12 .

Detailed ways

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, this invention is not limited to the following embodiment.

(first embodiment)

<Structure of Refrigeration Cycle Device>

FIG. 1 is a configuration diagram of a refrigeration cycle apparatus 1 using a fluid machine 8A according to a first embodiment of the present invention. This refrigeration cycle device 1 includes a working fluid circuit 7 for circulating a working fluid (refrigerant). The working fluid circuit 7 includes a main compressor 2, a radiator 3, an expander 4, an evaporator 5, and a compressor 6 as an auxiliary compressor. connected in this order. Carbon dioxide or chlorofluorocarbon alternatives, for example, can be used as working fluids.

The main compressor 2 has a compression mechanism part 2a and a motor 2b for driving the compression mechanism part 2a in a sealed container 2c storing lubricating oil, and the main compressor 2 compresses a working fluid to high temperature and high pressure. As the main compressor 2, for example, a scroll compressor or a rotary compressor can be used. The discharge port of the main compressor 2 is connected to the inlet of the radiator 3 via the first flow path 7a.

The radiator 3 dissipates heat and cools the working fluid compressed by the main compressor 2 to a high temperature and high pressure. The outlet of the radiator 3 is connected to the suction port of the expander 4 via the second flow path 7b.

The expander 4 expands the medium-temperature and high-pressure working fluid flowing out of the radiator 3, and converts the expansion energy of the working fluid into mechanical energy, thereby recovering power from the working fluid. In this embodiment, the expander 4 is constituted by a rotary expander (details will be described later). The discharge port of the expander 4 is connected to the inlet of the evaporator 5 via the third flow path 7c.

The evaporator 5 heats and evaporates the low-temperature and low-pressure working fluid expanded in the expander 4 . The outlet of the evaporator 5 is connected to the suction port of the compressor 6 via the fourth flow path 7d.

The compressor 6 pre-boosts the medium-temperature and low-pressure working fluid flowing out of the evaporator 5 and supplies it to the main compressor 2 . In this embodiment, the compressor 6 is constituted by a rotary compressor (details will be described later). The discharge port of the compressor 6 is connected to the suction port of the main compressor 2 via the fifth flow path 7e.

The expander 4 and the compressor 6 are arranged in a state of being connected to each other by a shaft 81 in a single airtight container 80 storing lubricating oil, thereby constituting a fluid machine 8A. That is, the power recovered by the expander 4 is transmitted to the compressor 6 via the shaft 81 to drive the compressor 6 .

Furthermore, the refrigeration cycle device 1 shown in FIG. 1 is provided with: a first bypass passage 91 connected to the working fluid circuit 7 at both ends in a manner bypassing the evaporator 5 and the compressor 6; The second bypass passage (equivalent to the bypass passage of the present invention) 93 connected to the working fluid circuit 7 at both ends. The first bypass valve 92 for controlling the circulation of the working fluid in the first bypass passage 91 is provided on the first bypass passage 91, and the first bypass valve 92 for controlling the circulation of the working fluid in the second bypass passage 93 is provided on the second bypass passage 93. The second bypass valve 94.

The first bypass passage 91 connects the third passage 7 c that guides the working fluid from the discharge port of the expander 4 to the inlet of the evaporator 5 and the fifth passage 7 c that guides the working fluid from the discharge port of the compressor 6 to the suction port of the main compressor 2 . The flow path 7e is connected. That is, the first bypass passage 91 is a flow passage that allows the working fluid discharged from the expander 4 to bypass the evaporator 5 and the compressor 6 and directly suck it into the main compressor 2 . In this embodiment, a check valve is used as the first bypass valve 92 . However, the first bypass valve 92 is not limited thereto, and an on-off valve or a three-way valve may be used.

The first bypass valve 92 releases the working fluid when the pressure of the working fluid on the downstream side (outlet side) of the first bypass valve 92 in the first bypass passage 91 is lower than the pressure of the working fluid on the upstream side (inlet side). The working fluid can flow through the first bypass passage 91 , and vice versa, the working fluid cannot flow through the first bypass passage 91 . That is, the pressure of the working fluid in the fifth flow path 7 e between the discharge port of the compressor 6 and the suction port of the main compressor 2 is lower than that of the flow between the discharge port of the expander 4 and the suction port of the compressor 6 . When the pressure of the working fluid in the channels (third channel 7c, evaporator 5, and fourth channel 7d) is maintained, the working fluid flows from the third channel 7c to the fifth channel 7e via the first bypass channel 91.

The second bypass passage 93 connects the second passage 7 b that guides the working fluid from the outlet of the radiator 3 to the suction inlet of the expander 4 and the fourth passage that guides the working fluid from the outlet of the evaporator 5 to the suction inlet of the compressor 6 . 7d connection. That is, the second bypass passage 93 is a flow passage that allows the high-pressure working fluid flowing out of the radiator 3 to bypass the expander 4 and the evaporator 5 and directly suck it into the compressor 6 . In this embodiment, an on-off valve is used as the second bypass valve 94 . However, the second bypass valve 94 is not limited thereto, and a three-way valve may also be used. In addition, the second bypass passage 93 only needs to be a flow passage that can directly suck the high-pressure working fluid into the compressor 6, and it may also be a passage that guides the working fluid from the discharge port of the main compressor 2 to the inlet of the radiator 3. The first flow path 7a is connected to the fourth flow path 7d.

When the second bypass valve 94 is opened during the startup control, the high-pressure working fluid flowing out of the radiator 3 flows from the second flow path 7 b into the fourth flow path 7 d via the second bypass path 93 .

In addition, in the refrigeration cycle device 1 shown in FIG. 1, between the outlet of the evaporator 5 in the fourth flow path 7d and the position where the downstream end of the second bypass path 93 is connected, a control fourth flow path 7d is provided. The compressor upstream valve 71 in the circulation of the working fluid. In this embodiment, an on-off valve is used as the compressor upstream valve 71 . The compressor upstream valve 71 is closed during startup control, thereby preventing the working fluid from flowing from the evaporator 5 to the compressor 6 and the working fluid flowing into the fourth flow path 7d through the second bypass passage 93 from flowing into the evaporator. 5 flow situation.

The second bypass valve 94 and the compressor upstream valve 71 are controlled by a control device (not shown). In addition, although not shown, the refrigeration cycle apparatus 1 is provided with an activation detection mechanism for detecting that the compressor 6 has been activated, and a detection signal is sent from the activation detection mechanism to the control device when the compressor 6 is activated. As such a start detection mechanism, for example, a method of measuring the temperature of the working fluid in the third flow path 7c by installing a thermocouple in the third flow path 7c on the discharge side of the expander 4 can be used.

<Operation of Refrigeration Cycle Device>

The refrigeration cycle apparatus 1 first performs start-up control, and then starts steady operation. In the refrigeration cycle device 1 , the pressure of the working fluid in the working fluid circuit 7 is substantially equalized in the standby state (stopped).

In the start control, first, the second bypass valve 94 is opened, and the compressor upstream valve 71 is closed. Thereby, the second bypass passage 93 is opened, and the fourth flow passage 7 d is closed between the outlet of the evaporator 5 and the downstream end of the second bypass passage 93 . Next, the main compressor 2 is activated, and the working fluid in the fifth flow passage 7 e and the working fluid in the first bypass passage 91 downstream of the first bypass valve 92 are sucked into the main compressor 2 .

When the working fluid starts to be sucked into the main compressor 2 , the pressure of the working fluid in the fifth flow passage 7 e and the working fluid in the first bypass passage 91 downstream of the first bypass valve 92 decreases. As a result, the first bypass valve 92 serving as a check valve is opened, and the flow paths from the discharge port of the expander 4 to the upstream valve 71 of the compressor (those of the third flow path 7c, the evaporator 5, and the fourth flow path 7d) are opened. The working fluid in part 1) flows into the first bypass passage 91 . That is, the working fluid in the flow path from the discharge port of the expander 4 to the compressor upstream valve 71 is sucked into the main compressor 2 together with the working fluid in the first bypass path 91 and the working fluid in the fifth flow path 7e. compressed, and discharged to the first flow path 7a. As a result, the pressures of the working fluid in the first bypass passage 91 on the upstream side of the first bypass valve 92 and the working fluid in the flow passage from the discharge port of the expander 4 to the compressor upstream valve 71 also decrease. reduce.

On the other hand, when the working fluid sucked into the main compressor 2 is compressed and discharged, the flow path from the discharge port of the main compressor 2 to the suction port of the expander 4 (the first flow path 7a, the radiator 3, The pressure of the working fluid in the second flow path 7b) rises. In addition, since the second bypass valve 94 is opened and the compressor upstream valve 71 is closed during start-up control, the working fluid in the flow path from the discharge port of the main compressor 2 to the suction port of the expander 4 passes through the second bypass valve. The passage 93 also flows into a portion between the compressor upstream valve 71 and the suction port of the compressor 6 in the fourth flow passage 7d. As a result, the pressure of the working fluid in the flow path (a part of the fourth flow path 7 d ) from the compressor upstream valve 71 to the suction port of the compressor 6 rises.

Therefore, between the working fluid (high pressure) in the suction port side flow path (second flow path 7 b ) of the expander 4 and the working fluid (low pressure) in the discharge port side flow path (third flow path 7 c ), and the compression High and low pressures are respectively generated between the working fluid (high pressure) in the suction port side flow path (a part of the fourth flow path 7d) of the machine 6 and the working fluid (low pressure) in the discharge port side flow path (fifth flow path 7e). Difference. The high and low pressure differences of the working fluid act on the expander 4 and the compressor 6 respectively, so that the fluid machine 8A can be easily self-started.

When the start detection mechanism detects that the compressor 6 has started, the second bypass valve 94 is closed and the compressor upstream valve 71 is opened. As a result, the second bypass passage 93 is closed, and the fourth flow passage 7d is opened. Then, the refrigeration cycle device 1 ends the start-up control, and shifts to a steady operation in which the working fluid is circulated in the working fluid circuit 7 .

During steady operation, the working fluid in the fourth flow path 7d and the working fluid in the second bypass passage 93 on the downstream side of the second bypass valve 94 are sucked into the compressor 6 to raise the pressure, and the pressure is increased to the fifth flow path. The flow path 7e is discharged. Accordingly, the pressure of the working fluid in the fifth flow path 7e and the pressure of the working fluid in the first bypass passage 91 on the downstream side of the first bypass valve 92 are higher than those from the discharge port of the expander 4 to the compressor. The pressure of the working fluid in the passage (the third passage 7c, the evaporator 5, and the fourth passage 7d) up to the suction port of 6, and the pressure in the first bypass passage 91 on the upstream side of the first bypass valve 92 The pressure of the working fluid closes the first bypass valve 92 of the check valve. During steady operation, the pressures of the working fluid in the fifth flow path 7e and the working fluid in the first bypass passage 91 on the downstream side of the first bypass valve 92 become high pressures as described above, so the first bypass valve Valve 92 remains closed. Thus, the working fluid in steady operation circulates in the working fluid circuit 7 .

<Structure of Fluid Machine>

Next, the structure of the fluid machine 8A will be described in detail. FIG. 2 is a longitudinal sectional view of the fluid machine 8A. 3 to 5 are transverse cross-sectional views of the fluid machine 8A corresponding to lines III-III to V-V in FIG. 2 . In addition, in FIGS. 3-5, the airtight container 80 is abbreviate|omitted.

As described above, the fluid machine 8A is a power recovery system in which the expander 4 and the compressor 6 are connected by the shaft 81 and the compressor 6 is driven by power recovered by the expander 4 . In this embodiment, the shaft 81 extends in the vertical direction, the expander 4 is arranged in the lower part of the airtight container 80 , and the compressor 6 is arranged in the upper part of the airtight container 80 . Wherein, the positional relationship between the expander 4 and the compressor 6 can be upside down, the shaft 81 can also extend in the transverse direction, and the expander 4 and the compressor 6 can also be arranged in the transverse direction. In addition, lubricating oil is filled in the airtight container 80 to such an extent that the oil level is located above the compressor 6 .

1) axis

The shaft 81 is located at a position away from the axis center of the shaft 81 as a central axis. The eccentric portion includes a first eccentric portion 81 b for the expander 4 and a second eccentric portion 81 c for the compressor 6 . The shaft 81 is formed with an oil supply passage 81a passing through the shaft 81 in the axial direction and opening on the outer peripheral surface of the first eccentric portion 81b, the outer peripheral surface of the second eccentric portion 81c, and the like. The lubricating oil in the airtight container 80 is supplied to the slide portion of the expander 4 or the compressor 6 through the oil supply passage 81 a.

2) Expander

As described above, in this embodiment, the expander 4 is constituted by a rotary expander. However, the expander 4 is not limited to a rotary expander, and may be a scroll expander or other types of expanders. The expander 4 recovers power from the working fluid by expanding the working fluid sucked in from the expander suction hole 4 a and discharging it from the expander discharge hole 4 b.

Specifically, as shown in FIG. 4 , the expander 4 includes an expander piston 42 fitted to the first eccentric portion 81 b of the shaft 81 , and an expander cylinder 41 that accommodates the expander piston 42 . The expander cylinder 41 has an inner peripheral surface forming a cylindrical surface whose central axis coincides with the axis of the shaft 81 , and the expander piston 42 eccentrically rotates along the inner peripheral surface of the expander cylinder 41 as the shaft 81 rotates. sports. That is, a crescent-shaped expander working chamber 43 is formed between the inner peripheral surface of the expander cylinder 41 and the outer peripheral surface of the expander piston 42 .

The expander working chamber 43 is divided into a suction side 43 a and a discharge side 43 b by an expander partition member 44 . The expander suction hole 4 a opens at a portion of the suction side 43 a adjacent to the expander partition member 44 , and the expander discharge hole 4 b opens at a portion of the discharge side 43 b adjacent to the expander partition member 44 .

The expander partition member 44 has a plate shape and is reciprocally inserted into a groove 41 a provided in the expander cylinder 41 . The groove 41 a opens to the expander working chamber 43 on a straight line passing through the axis of the shaft 81 . An urging mechanism 45 for pressing the expander partition member 44 against the outer peripheral surface of the expander piston 42 is disposed between the bottom of the groove 41 a and the expander partition member 44 .

The urging mechanism 45 can be constituted by, for example, a compression coil spring. In addition, the urging mechanism 45 may be a so-called gas spring that forms a back space between the rear end of the expander partition member 44 and the bottom of the groove 41a as a closed space. Of course, various springs such as compression coil springs and gas springs can also be used to form the force applying mechanism 45 . It should be noted that the expander piston 42 and the expander partition member 44 may be integrally formed without the urging mechanism 45 .

In addition, as shown in FIG. 2 , the expander 4 has a first closing member (inner closing member) 49 that closes the expander working chamber 43 from the compressor 6 side, and a first closing member (inner closing member) 49 that closes the expander working chamber 43 from the side opposite to the compressor 6 . The second blocking member (outer blocking member) 46 and the bearing member 47 arranged below the second blocking member 46 .

The bearing member 47 is fixed to the inner peripheral surface of the airtight container 80, and supports the lower part of the shaft 81 so that rotation is possible. The second closing member 46 , the expander cylinder 41 , and the first closing member 49 are stacked on the bearing member 47 in this order. Furthermore, a suction pipe 82 and a discharge pipe 83 penetrating through the airtight container 80 are connected to the bearing member 47 .

Both the first closing member 49 and the second closing member 46 are formed in a flat disk shape in the axial direction of the shaft 81 , and the shaft 81 penetrates through the centers of the first closing member 49 and the second closing member 46 . In this embodiment, the expander suction hole 4 a is provided in the second closing member 46 , and the expander discharge hole 4 b is provided in the first closing member 49 and the expander cylinder 41 .

On the lower surface of the second blocking member 46, a circular concave portion 46a whose center coincides with the axis of the shaft 81 is provided, and the expander suction hole 4a extends straight from the upper surface of the second blocking member 46 to the bottom surface of the concave portion 46a. The second blocking member 46 passes through in the axial direction of the shaft 81 . The expander suction hole 4 a communicates with the suction pipe 82 via the suction space in the recess 46 a and the suction passage 47 a formed in the bearing member 47 . That is, the high-pressure working fluid from the second flow path 7b shown in FIG. 1 is guided from the expander suction hole 4a to the suction side 43a of the expander working chamber 43 through the suction pipe 82, the suction path 47a, and the suction space in the concave portion 46a. .

On the other hand, as shown in FIG. 4, the expander discharge hole 4b is composed of a vertical groove 41b and a horizontal groove 49a, wherein the vertical groove 41b is formed on the inner peripheral surface of the expander working cylinder 41, and extends outward in the radial direction. The horizontal groove 49 a is formed on the lower surface of the first blocking member 49 so as to extend radially outward from a position corresponding to the vertical groove 41 b. The outer end of the expander discharge hole 4b communicates with the discharge pipe 83 via the discharge passage 4c formed to extend across the expander cylinder 41 , the second closing member 46 and the bearing member 47 . That is, the working fluid in the discharge side 43b of the expander working chamber 43 is discharged to the third flow passage 7c shown in FIG. 1 through the expander discharge hole 4b, the discharge passage 4c, and the discharge pipe 83 .

Furthermore, a rotary plate 48 is disposed in the recess 46 a as a suction control mechanism that opens and closes the expander suction hole 4 a as the shaft 81 rotates. The rotating plate 48 is attached to the shaft 81 so as to rotate while being in contact with the bottom surface of the concave portion 46a.

As shown in FIG. 4 , the expander suction hole 4 a extends in an arc shape along the inner peripheral surface of the expander cylinder 41 from the vicinity of the expander partition member 44 . As shown in FIG. 3 , the rotating plate 48 has a large-diameter portion 48a that blocks the expander suction hole 4a, and a small-diameter portion 48b that exposes the expander suction hole 4a.

In this embodiment, depending on the angular range and position of the large-diameter portion 48a and the small-diameter portion 48b, the expander suction hole 4a is partially or completely exposed when the expander piston 41 rotates from the top dead center to about 140°. In other periods, the expander suction hole 4a is completely covered by the large diameter portion 48a. Here, the top dead center refers to a position where the sliding point of the expander piston 42 that slides on the inner peripheral surface of the expander cylinder 41 coincides with the expander partition member 44 .

It should be noted that the structure of the expander 4 can be reversed up and down. That is, the first blocking member 49, the expander cylinder 41, the second blocking member 46, the rotating plate 48, and the bearing member 47 may be arranged in this order from bottom to top, so that the first blocking member 49 becomes an outer blocking member, and the second blocking member 49 becomes an outer blocking member. The blocking member 46 becomes an inner blocking member. In this case, the shaft 81 may be loosely fitted to the bearing member 47 so that the first closing member 49 may have the function of supporting the lower portion of the shaft 81 in a rotatable manner.

3) Compressor

As described above, in the present embodiment, the compressor 6 is a rotary compressor. The compressor 6 boosts the pressure of the working fluid sucked in from the compressor suction hole 6a and discharges it from the compressor discharge hole 6b.

Specifically, as shown in FIG. 5 , the compressor 6 has a compressor piston 62 fitted to the second eccentric portion 81 c of the shaft 81 , and a compressor cylinder 61 for accommodating the compressor piston 62 . The compressor cylinder 61 has an inner peripheral surface forming a cylindrical surface whose central axis coincides with the axis of the shaft 81, and the compressor piston 62 rotates eccentrically along the inner peripheral surface of the compressor cylinder 61 as the shaft 81 rotates. sports. That is, a crescent-shaped compressor working chamber 63 is formed between the inner peripheral surface of the compressor cylinder 61 and the outer peripheral surface of the compressor piston 62 .

The compressor working chamber 63 is partitioned into a suction side 63 a and a discharge side 63 b by a compressor partition member 64 . The compressor suction hole 6 a opens at a portion of the suction side 63 a adjacent to the compressor partition member 64 , and the compressor discharge hole 6 b opens at a portion of the discharge side 63 b adjacent to the compressor partition member 64 .

The compressor partition member 64 has a plate shape and is reciprocally inserted into the groove 61 a provided in the compressor cylinder 61 . The groove 61 a opens to the compressor working chamber 63 on a straight line passing through the center of the shaft 81 . A urging mechanism 65 for pressing the compressor partition member 64 against the outer peripheral surface of the compressor piston 62 is disposed between the bottom of the groove 61 a and the compressor partition member 64 .

The urging mechanism 65 can be constituted by, for example, a compression coil spring. In addition, the urging mechanism 65 may be a so-called gas spring or the like which makes the back space between the rear end of the compressor partition member 64 and the bottom of the groove 61a a closed space. Certainly, the force applying mechanism 65 may be composed of various springs such as compression coil springs and gas springs. In addition, the compressor piston 62 may be integrally formed with the compressor partition member 64 without the urging mechanism 65 .

In addition, as shown in FIG. 2 , the compressor 6 has a first closing member (inner closing member) 49 that closes the compressor working chamber 63 from the expander 4 side, and a second closing member (inner closing member) 49 that closes the compressor working chamber 63 from the opposite side of the expander 4 . The second blocking member (outer blocking member) 66 and the cover member 67 arranged above the second blocking member 46 . That is, in the present embodiment, the expander 4 and the compressor 6 share the first closing member 49 . However, the expander 4 and the compressor 6 may each have a first closing member.

The second closing member 66 also has a function as a bearing member that rotatably supports the upper portion of the shaft 81 . The compressor cylinder 61 , the second closing member 66 and the cover member 67 are stacked on the first closing member 49 in this order. Furthermore, a suction pipe 84 penetrating through the airtight container 80 is connected to the compressor cylinder 61 , and a discharge pipe 85 penetrating the airtight container 80 is connected to the second closing member 66 .

The second blocking member 66 is formed in a flat disc shape in the axial direction of a shaft 81 penetrating through the center of the second blocking member 66 . The cover member 67 is also formed in the shape of a disk flattened in the axial direction of the shaft 81 , and has an opening at its center that exposes the upper end of the shaft 81 . In the present embodiment, a compressor suction hole 6 a is provided in the compressor cylinder 61 , and a compressor discharge hole 6 b is provided in the second closing member 66 .

The compressor suction hole 6 a penetrates the compressor cylinder 61 in the lateral direction, opens in a substantially circular shape on the inner peripheral surface of the compressor cylinder 61 , and communicates with the suction pipe 84 . That is, the working fluid of low pressure (high pressure during startup control) from the fourth flow path 7d shown in FIG.

Since the compressor suction hole 6a opens on the inner peripheral surface of the compressor cylinder 61, it is opened and closed by the compressor piston 62 as the shaft rotates. More specifically, the compressor suction hole 6a is closed by the compressor piston 62 while the sliding point of the compressor piston 62 sliding on the inner peripheral surface of the compressor cylinder 61 is located on the compressor suction hole 6a, in other words, When the top dead center (the position where the sliding point of the compressor piston 62 coincides with the compressor partition member 64 ) is 0°, the compressor piston 62 is closed by the compressor piston 62 while the compressor piston 62 rotates from about 5° to about 15°. It should be noted that the diameter of the inner peripheral surface of the compressor working cylinder 61 is different from the diameter of the outer peripheral surface of the compressor piston 62, so the compressor suction hole 6a will not be completely closed by the compressor piston 62, but in this specification In , it is defined that the compressor suction hole 6a is closed while the sliding point of the compressor piston 62 is located on the compressor suction hole 6a as described above.

On the other hand, a discharge chamber 66 a opened on the upper surface and closed by the cover member 67 , and a discharge passage 66 b from the discharge chamber 66 a to the discharge pipe 85 are formed in the second closing member 66 . The compressor discharge hole 6b extends straight from the lower surface of the second closing member 66 to the discharge chamber 66a with a circular cross section penetrating the second closing member 66 in the axial direction of the shaft 81, and passes through the discharge chamber 66a and the discharge passage 66b. It communicates with the discharge pipe 85 . That is, the working fluid in the discharge side 63b of the compressor working chamber 63 is discharged to the fifth flow passage 7e shown in FIG. 1 through the compressor discharge hole 6b, discharge chamber 66a, discharge passage 66b, and discharge pipe 85.

In the present embodiment, since the compressor discharge hole 6b is arranged at a position crossed by the inner peripheral surface of the compressor cylinder 61, the compressor piston 62 is positioned on the compressor discharge hole 6b while the sliding point of the compressor piston 62 is located on the compressor discharge hole 6b. The discharge hole 6b is closed by the compressor piston 62, in other words, the compressor discharge hole 6b is closed by the compressor piston 62 while the compressor piston 62 rotates from approximately 345° to approximately 355° when the top dead center is set to 0°. It should be noted that, similarly to the compressor suction hole 6a, the compressor discharge hole 6b is not completely closed by the compressor piston 62, but in this specification, it is defined as the sliding point of the compressor piston 62 as described above. The compressor discharge hole 6b is closed while being located on the compressor discharge hole 6b.

In addition, a discharge valve 68 is arranged in the discharge chamber 66 a, and the discharge valve 68 automatically opens and closes the compressor discharge hole 6 b under the pressure of the discharge side 63 b of the compressor working chamber 63 by elastic deformation.

As described above, by forming the compressor suction hole 6a, the flow path resistance of the working fluid flowing into the compressor working chamber 63 can be reduced, and the pressure drop of the working fluid sucked into the compressor 6 can be suppressed. In addition, as described above, by forming the compressor discharge hole 6b, the structure of the compressor 6 can be simplified, the flow path resistance of the working fluid flowing out from the compressor working chamber 63 can be reduced, and the work fluid discharged from the compressor 6 can be suppressed. A decrease in the pressure of the fluid.

It should be noted that the structure of the compressor 6 can be reversed up and down. That is, the cover member 67, the second blocking member 66, the compressor cylinder 61, and the first blocking member 49 may be arranged in this order from bottom to top, so that the first blocking member 49 becomes an outer blocking member, and the second blocking member 66 Become the medial occlusive member. In this case, the shaft 81 may be loosely fitted to the second blocking member 66 so that the first blocking member 49 may function to rotatably support the upper portion of the shaft 81 .

4) Mutual relationship

The fluid machine 8A is configured so that the expander suction hole 4a is kept open while the compressor suction hole 6a is closed, and the compressor suction hole 6a is kept open while the expander suction hole 4a is closed. And the state of not communicating with the compressor discharge hole 4b. Specifically, the shaft 81, the expander 4, and the compressor 6 are configured such that the compressor piston 62 passes through the top dead center while the expander suction hole 4a is open.

In order to achieve the above-mentioned mutual relationship, it is preferable that the phase difference of the eccentric direction of the second eccentric portion 81c relative to the eccentric direction of the first eccentric portion 81b when the rotational direction of the shaft 81 is set as a timing is βc (wherein -180°<βc ≤180°), the phase difference of the position of the compressor partition member 64 relative to the position of the expander partition member 44 is βv (wherein, -180°<βv≤180°), and the phase difference of the shaft during the opening of the expander suction hole 6a When the rotation angle is θo, Expression 1 below is satisfied.

0.25θo≤βv-βc≤0.75θo...(Formula 1)

In this embodiment, as shown in FIG. 4 and FIG. 5 , the position of the expander partition member 44 and the position of the compressor partition member 64 coincide with the axial direction of the shaft 81, and the eccentric direction of the second eccentric portion 81c is relative to that of the second eccentric portion 81c. The eccentric direction of one eccentric portion 81b is shifted by -90°. That is, βc=-90°, βv=0°, and βv-βc=90°. In addition, from the shape of the rotating plate 48 as described above, θo=approximately 140°. Thus, 0.25θo≈35° and 0.75θo≈105°, which satisfy Equation 1.

It should be noted that the present invention is not limited thereto. For example, the first eccentric portion 81b and the second eccentric portion 81c may be eccentric in the same direction, and the position of the expander partition member 44 and the position of the compressor partition member 64 may be varied within the range satisfying Formula 1, or the eccentric direction and the partition may be Both of the positions of the members vary within the range satisfying Expression 1.

<Motion of Fluid Machinery>

Next, the operation of the fluid machine 8A in steady operation will be described with reference to FIGS. 6A to 6C and FIGS. 7A to 7C . In the above figure, the rotation angle θ of the shaft 81 when the expander piston 42 is at the top dead center is assumed to be 0°.

First, the operation of the expander 4 will be described. As shown in FIGS. 6A to 6C , the shaft 81 starts to rotate from θ=0°, and the rotating plate 48 rotates synchronously with this, whereby the expander suction hole 4a starts to protrude from the rotating plate 48, and the expander suction hole 4a opens. Then, the high-pressure working fluid from the radiator 3 is sucked into the suction side 43a of the expander working chamber 43 through the expander suction hole 4a. After that, the expander suction hole 4a is completely exposed when the shaft 81 is rotated by about 30°. On the other hand, as shown in FIGS. 7A and 7B , the rotating plate 48 begins to block the expander suction hole 4a when the shaft 81 rotates about 125°, and the expander suction hole 4a is completely blocked when the shaft 81 rotates about 140°. The expander suction hole 4a is closed. Thus, the suction stroke ends.

Thereafter, as shown in FIG. 7C , as the shaft 81 rotates, the volume of the suction side 63 a of the expander working chamber 63 gradually increases, whereby the working fluid expands and torque is applied to the shaft 81 . And, the torque applied to the shaft 81 is utilized as the motive power of the compressor 6 . The shaft 81 rotates 360° and the expander piston 42 passes the top dead center, whereby the suction side 43a of the expander working chamber 43 turns to the discharge side 43b, and then the shaft 81 rotates one revolution, whereby the expanded working fluid passes through the discharge side 43b The expander discharge hole 4b is discharged toward the evaporator 5 .

Next, the operation of the compressor 6 will be described. The shaft 81 is rotated by power recovered by the expander 4 . Simultaneously with the rotation of the shaft 81, the compressor piston 62 also rotates, and the compressor 6 is driven.

As shown in FIGS. 6C and 7A, when the shaft 81 rotates about 105°, the compressor suction hole 6a opens, and the low-pressure working fluid from the evaporator 5 passes through the compressor suction hole 6a to the suction side of the compressor working chamber 63. 63a inhalation. And, the compressor piston 62 further rotates, and after the suction side 63a of the compressor working chamber 63 communicates with the compressor discharge hole 6b, the compressor piston 62 passes through the top dead center, and thus the suction side 63a of the compressor working chamber 63 moves toward the discharge side. 63b transition, at this time, with the rotation of the shaft 81, the volume of the discharge side 63b of the compressor working chamber 63 gradually decreases. As a result, the working fluid in the discharge side 63b of the compressor working chamber 63 is compressed to increase its pressure. And, when the pressure of the working fluid in the discharge side 63b of the compressor working chamber 63 becomes higher than the pressure of the working fluid in the discharge chamber 66a, the working fluid in the discharge side 63b presses the discharge valve 68 to be discharged through the compressor. It is discharged toward the main compressor 2 through the hole 6b.

<Functions and effects of this embodiment>

In the present embodiment, as described above, the period during which the expander suction hole 4a is open is θ=0° to about 140°, and the period during which the expander suction hole 4a is closed is θ=about 140° to 360°. On the other hand, the closed period of the compressor suction hole 6a is θ = about 95° to about 105°, and the period for the compressor suction hole 6a to be opened is θ = 0° to about 95° and θ = about 105 to 360°. In addition, the period during which the compressor discharge hole 6b communicates with the compressor discharge hole 6b via the compressor working chamber 63 is θ=about 85° to about 95°. That is, the expander suction hole 4a is closed after the compressor suction hole 6a communicates with the suction side 63a of the compressor working chamber 63, and the expander suction hole 4a is closed before the suction side 63a of the compressor working chamber 63 communicates with the compressor discharge hole 6b. Open.

As described in the column <Operation of Refrigeration Cycle Device>, when the refrigeration cycle device 1 is started, the main compressor 2 is started with the second bypass valve 94 open and the compressor upstream valve 71 closed, so the expansion Between the working fluid in the flow path on the suction side of the compressor 4 and the working fluid in the flow path on the discharge side of the compressor 4, and between the working fluid in the flow path on the suction side of the compressor 6 and the working fluid in the flow path on the discharge side There is a high and low pressure difference between them. In other words, the upstream flow path of the expander suction hole 4 a passing through the suction pipe 82 of the fluid machine 8A and the upstream flow path of the compressor suction hole 6 a passing through the suction pipe 84 are filled with high-pressure working fluid.

In the present embodiment, since the fluid machine 8A is configured as described above, when the refrigeration cycle device 1 is started, no matter what angular position the shaft 81 of the fluid machine 8A is at, there is always a hole in the expander suction hole 4a or the compressor suction hole 6a. At least one of them is open, and high-pressure working fluid always flows into at least one of the suction side 43 a of the expander working chamber 43 or the suction side 63 a of the compressor working chamber 63 . In addition, the communication of the compressor suction hole 6a with the compressor discharge hole 6b via the compressor working chamber 63 is after the expander suction hole 4a is opened. Therefore, regardless of the state in which the fluid machine 8A stops, one or both of the expander 4 and the compressor 6 can generate torque for rotating the shaft 81, so that the fluid machine 8A can be self-started under the pressure of the working fluid. .

Specifically, when the shaft 81 is located in the range of θ=0° to approximately 85°, since both the expander suction hole 4a and the compressor suction hole 6a are open, the high-pressure working fluid is sucked into the expander working chamber 43 side 43 a and the suction side 63 a of the compressor working chamber 63 flow in, thus generating torque on the expander 4 and compressor 6 .

When the shaft 81 is located in the range of θ=about 85° to about 95°, the compressor suction hole 6a is closed, but communicates with the compressor discharge hole 6b via the compressor working chamber 63, and the working fluid flows from the compressor suction hole 6a. Since it flows to the compressor discharge hole 6 b, no torque is generated in the compressor 6 . However, since the expander suction hole 4 a is opened, the high-pressure working fluid flows into the suction side of the expander working chamber 63 , and torque is generated in the expander 4 .

In the case where the axis 81 is located in the range of θ=approximately 95° to 105°. The compressor suction hole 6a is closed, and no torque is generated on the compressor 6, but since the expander suction hole 4a is opened, the high-pressure working fluid flows into the suction side 63a of the compressor working chamber 63, thus generating torque on the compressor 6. moment.

When the shaft 81 is located in the range of θ=about 105° to about 140°, since the expander suction hole 4a and the compressor suction hole 6a are both open, the high-pressure working fluid flows to the suction side 43a of the expander working chamber 43 and The suction side 63 a of the compressor working chamber 63 flows in, so torque is generated in the expander 4 and the compressor 6 .

When the shaft 81 is located in the range of θ=approximately 140° to 360°, the expander suction hole 4a is closed, and no torque is generated on the expander 4, but since the compressor suction hole 6a is opened, the high-pressure working fluid flows to The suction side 63 a of the compressor working chamber 63 flows in, thus generating a torque on the compressor 6 .

In this way, in this embodiment, when the refrigeration cycle device 1 is started, the fluid machine 8A without a drive device can be reliably self-started only by the pressure of the working fluid, and the reliability of the refrigeration cycle device 1 can be improved.

(second embodiment)

Next, a fluid machine 8B according to a second embodiment of the present invention will be described with reference to FIGS. 8 and 9 . In addition, in this embodiment, the same code|symbol is attached|subjected to the same structural part as 1st Embodiment, and description is abbreviate|omitted. In addition, since the refrigeration cycle apparatus using the fluid machine 8B is the same as the refrigeration cycle apparatus 1 shown in FIG. 1, description is also abbreviate|omitted.

<Structure of Fluid Machine>

The fluid machine 8B of this embodiment differs from the fluid machine 8A of the first embodiment in that the suction pipe 84 is connected to the second closing member 66, and that the compressor 6 does not have the discharge valve 68 (see FIG. Fluid pressure motor compressor. That is, the compressor 6 boosts the pressure of the working fluid without changing the volume of the working fluid.

Specifically, the compressor suction hole 6a is provided on the second closing member 66 so as to be exposed only to the suction side 63a of the compressor working chamber 63, and the compressor discharge hole 6b is provided so as to be exposed only to the discharge side 63b of the compressor working chamber 63. The exposed manner is provided on the second blocking member 66 . Both the compressor suction hole 6 a and the compressor discharge hole 6 b extend in the axial direction of the shaft 81 . In addition, a suction passage 6c connecting the upper end of the compressor suction hole 6a to the suction pipe 84 and a discharge passage 6d connecting the upper end of the compressor discharge hole 6b to the discharge pipe 85 are formed on the second closing member 66 .

More specifically, the compressor suction hole 6 a and the compressor discharge hole 6 b extend from the vicinity of the compressor partition member 64 so as to be gradually separated from the inner peripheral surface of the compressor cylinder 61 . In addition, the outer sides of the compressor suction hole 6a and the compressor discharge hole 6b (sides on the inner peripheral surface side of the compressor cylinder 61) are formed to be aligned with the outer circumference of the compressor piston 62 when the compressor piston 62 is at the top dead center. The surface is uniformly arc-shaped. That is, the compressor suction hole 6a is completely closed by the compressor piston 63 shortly after the compressor piston 62 is positioned at the top dead center, and the compressor discharge hole 6b is closed by the compressor piston shortly before the compressor piston 62 is positioned at the top dead center. 63 is fully closed.

In addition, in this embodiment, the relationship between the eccentric direction of the first eccentric portion 81b and the eccentric direction of the second eccentric portion 82b of the shaft 81, the relationship between the position of the expander partition member 44 and the position of the compressor partition member 64 and The first embodiment is the same.

It should be noted that the compressor suction hole 6 a and the compressor discharge hole 6 b do not necessarily need to be provided on the second blocking member 66 , and either one or both of them may be provided on the first blocking member 49 .

<Motion of fluid machine 8B>

Next, the operation of the fluid machine 8A in steady operation will be described with reference to FIGS. 10A to 10C and FIGS. 11A to 11C. In the above figure, the rotation angle θ of the shaft 81 when the expander piston 42 is at the top dead center is assumed to be 0°. In addition, since the operation|movement of the expander 4 is the same as that of 1st Embodiment, the description is abbreviate|omitted.

As shown in FIG. 10C and FIGS. 11A to 11C , the compressor suction hole 6 a is completely closed by the compressor piston 62 while the shaft 81 rotates from 90° to about 95°. After the shaft 81 rotates about 95°, the compressor suction hole 6a gradually opens, and the low-pressure working fluid from the evaporator 5 is sucked into the suction side 63a of the compressor suction working chamber 63 through the compressor suction hole 6a. After that, as shown in FIGS. 10A and 11B , after the compressor piston 62 rotates to about 360°, the compressor suction hole 6a is gradually closed. When the shaft 81 is rotated to 90° again, the suction stroke ends. The suction side 63a of the compressor working chamber 63 transitions to the discharge side 63b. After the shaft 81 is rotated by 90°, the compressor discharge hole 6b is gradually opened, and the working fluid in the discharge side 63b is discharged toward the main compressor 2 through the compressor discharge hole 6b. The pressure of the working fluid is boosted by the pressing of the working fluid by the compressor piston 62 . The compressor discharge hole 6b is gradually closed after the shaft 81 rotates about 300°, and is completely closed by the compressor piston 62 while the shaft 81 rotates from about 85° to 90°.

<Functions and effects of this embodiment>

In the present embodiment, as described above, the period during which the expander suction hole 4a is open is θ=0° to about 140°, and the period during which the expander suction hole 4a is closed is θ=about 140° to 360°. On the other hand, the period during which the compressor suction hole 6a is closed is θ=90° to about 95°, and the period during which the compressor suction hole 6a is open is θ=0° to 90° and θ=about 95° to 360°. That is, the expander suction hole 4a is closed after the compressor suction hole 6a communicates with the suction side 63a of the compressor working chamber 63, and the expander suction hole 4a is opened before the compressor suction hole 6a is closed.

As described in the column <Operation of Refrigeration Cycle Device>, when the refrigeration cycle device 1 is started, the main compressor 2 is started with the second bypass valve 94 opened and the compressor upstream valve 71 closed, so the expander Between the working fluid in the suction port side flow path of 4 and the working fluid in the discharge port side flow path, and between the working fluid in the suction port side flow path of compressor 6 and the working fluid in the discharge port side flow path Generate high and low pressure differences respectively. In other words, the upstream flow path of the expander suction hole 4 a passing through the suction pipe 82 of the fluid machine 8A and the upstream flow path of the compressor suction hole 6 a passing through the suction pipe 84 are filled with high-pressure working fluid.

In the present embodiment, since the fluid machine 8A is configured as described above, when the refrigeration cycle apparatus 1 is started, regardless of the angular position of the shaft 81 of the fluid machine 8A, at least one of the expander suction hole 4a or the compressor suction hole 6a One side is always open, and high-pressure working fluid always flows into at least one of the suction side 43 a of the expander working chamber 43 or the suction side 63 a of the compressor working chamber 63 . Therefore, regardless of the state in which the fluid machine 8A is stopped, a torque for rotating the shaft 81 can be generated in one or both of the expander 4 and the compressor 6, so that the fluid machine 8A can be self-started by the pressure of the working fluid. .

Specifically, when the shaft 81 is located in the range of θ=0° to 90°, since both the expander suction hole 4 a and the compressor suction hole 6 a are open, the high-pressure working fluid flows to the suction side of the expander working chamber 43 . 43a and the suction side 63a of the compressor working chamber 63 flow in, so the expander 4 and the compressor 6 generate torque.

When the axis 81 is located in the range of θ=90° to approximately 95°, the compressor suction hole 6a is closed, and no torque is generated in the compressor 6, but since the expander suction hole 4a is opened, the high-pressure working fluid is compressed Since the suction side 63a of the engine working chamber 63 flows in, torque is generated in the compressor 6 .

When the shaft 81 is located in the range of θ=about 95° to about 140°, since the expander suction hole 4a and the compressor suction hole 6a are both open, the high-pressure working fluid flows to the suction side 43a of the expander working chamber 43 and Since the suction side 63 a of the compressor working chamber 63 flows in, torque is generated by the expander 4 and the compressor 6 .

When the shaft 81 is located in the range of θ=approximately 140° to 360°, the expander suction hole 4a is closed, and no torque is generated in the expander 4, but since the compressor suction hole 6a is opened, the high-pressure working fluid is compressed Since the suction side 63a of the engine working chamber 63 flows in, torque is generated in the compressor 6 .

In this way, in this embodiment, when the refrigeration cycle device 1 is started, the pressure of the working fluid can reliably self-start the fluid machine 8A without a drive device, thereby improving the reliability of the refrigeration cycle device 1 .

(Other implementations)

In the above embodiment, the suction control mechanism that opens and closes the expander suction hole 4a as the shaft 81 rotates is constituted by the rotating plate 48, but the suction control mechanism of the present invention is not limited to this, and various configurations can be adopted. For example, the suction control mechanism with the structure disclosed in Patent Document 1 may be adopted, and an arc groove may be provided on the upper surface of the first eccentric portion 81b of the shaft 81, and a communication station may be provided on the lower surface of the first blocking member 49. The suction control mechanism of the communication groove between the circular arc groove and the suction side 43a of the expander working chamber 43 is described.

Industrial availability

The invention can reliably realize the self-starting of the fluid machine, and is especially useful in a refrigeration cycle device in which the fluid machine is used as a power recovery system.

Claims (10)

1. fluid machinery, it possesses:

Decompressor, it makes from the working fluid expansion of decompressor inlet hole suction and from the decompressor tap hole and discharges, and reclaims power from working fluid thus;

Compressor, it boosts the working fluid that sucks from the compressor inlet hole and discharges from the compressor tap hole;

Axle, it links said decompressor and said compressor, thereby utilizes the power that is reclaimed by said decompressor to drive said compressor,

Said decompressor inlet hole and said compressor inlet hole open and close along with the rotation of said axle,

Said fluid machinery is maintained in; In said compressor inlet hole closed period; Said decompressor inlet hole is in the state of opening, and in said decompressor inlet hole closed period, said compressor inlet hole is in state of opening and the state that is not communicated with said compressor tap hole.

2. fluid machinery according to claim 1, wherein,

Said axle has second eccentric part that first eccentric part that said decompressor uses and said compressor are used,

Said compressor comprises: and the chimeric compressor piston of said second eccentric part, accommodate said compressor piston the compressor operating cylinder, will be formed on the compressor partition member that compressor operating chamber between said compressor piston and the said compressor operating cylinder is separated into the suction side and discharges side

Said decompressor inlet hole open during in, said compressor piston is through the sliding point that on the inner peripheral surface of said compressor operating cylinder, slides and the consistent top dead center of said compressor partition member of this compressor piston.

3. fluid machinery according to claim 2, wherein,

Said decompressor comprises: the decompressor piston chimeric with said first eccentric part; Accommodate the decompressor clutch release slave cylinder of said decompressor piston; The decompressor working room that is formed between said decompressor piston and the said decompressor clutch release slave cylinder is separated into suction side and the decompressor partition member of discharging side,

The eccentric direction that is made as said second eccentric part in correct time in the sense of rotation with said axle is that the position of β c, said compressor partition member is that the angle of swing of the said axle during β v and said decompressor inlet hole are opened is θ o with respect to the phase difference of the position of said decompressor partition member with respect to the phase difference of the eccentric direction of said first eccentric part; Wherein,-180 °＜β c≤180 °; During-180 °＜β v≤180 °

Satisfy 0.25 θ o≤β v-β c≤0.75 θ o.

4. according to claim 2 or 3 described fluid machineries, wherein,

Said compressor inlet hole is arranged on the said compressor operating cylinder and in the inner peripheral surface upper shed of said compressor operating cylinder,

With after the suction side of said compressor operating chamber is communicated with, said decompressor inlet hole is closed at said compressor inlet hole, and with before said compressor tap hole is communicated with, said decompressor inlet hole is opened in the suction side of said compressor operating chamber.

5. fluid machinery according to claim 4, wherein,

Said compressor comprises that also the pressure of the discharge side of utilizing said compressor operating chamber opens and closes the expulsion valve of said compressor tap hole.

6. according to claim 2 or 3 described fluid machineries, wherein,

Said compressor also comprises: from the inboard obstruction component of the inaccessible said compressor operating of said expander side chamber; From the outside obstruction component of the inaccessible said compressor operating of the opposition side of said decompressor chamber,

Said compressor inlet hole is arranged on said inboard obstruction component or the said outside obstruction component with the mode of only exposing to the suction side of said compressor operating chamber,

With after the suction side of said compressor operating chamber is communicated with, said decompressor inlet hole is closed at said compressor inlet hole, and said decompressor inlet hole is opened before said compressor inlet hole is closed.

7. fluid machinery according to claim 6, wherein,

Said compressor tap hole is only to be arranged on said inboard obstruction component or the said outside obstruction component to the mode that the discharge side of said compressor operating chamber is exposed.

8. fluid machinery according to claim 3, wherein,

Said decompressor also comprises the suction control mechanism that opens and closes said decompressor inlet hole along with the rotation of said axle.

9. fluid machinery according to claim 8, wherein,

Said decompressor also comprises: from the inboard obstruction component of the inaccessible said decompressor of said compressor side working room; From the outside obstruction component of the inaccessible said decompressor of the opposition side of said compressor working room,

Said decompressor inlet hole is arranged on this inboard obstruction component or this outside obstruction component with the mode that connects said inboard obstruction component or said outside obstruction component,

Said suction control mechanism is a swivel plate; This swivel plate is installed on the said axle with the mode that when the face with the said decompressor working room opposition side of said inboard obstruction component or said outside obstruction component joins, is rotated, and the minor diameter part that has the large-diameter portion that blocks said decompressor inlet hole and said decompressor inlet hole is exposed.

10. refrigerating circulatory device, it has used each described fluid machinery in the claim 1～9, and it possesses:

Operating fluid loop; It makes working fluid cycles, comprise compression working fluid main compressor, make the working fluid heat radiation after the compression radiator, make said decompressor that the working fluid that flows out from said radiator expands, make the vaporizer of the working fluid evaporation after the expansion and will boost from the working fluid that said vaporizer flows out and the said compressor supplied with to said main compressor;

Bypass, it is connected the part between the part between the said main compressor in the said operating fluid loop and the said radiator or said radiator and the said decompressor and said vaporizer with part between the said compressor.

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