WO2011135779A1

WO2011135779A1 - Fluid machine and refrigeration cycle apparatus

Info

Publication number: WO2011135779A1
Application number: PCT/JP2011/002050
Authority: WO
Inventors: 和田賢宣; 尾形雄司; 塩谷優
Original assignee: パナソニック株式会社
Priority date: 2010-04-30
Filing date: 2011-04-06
Publication date: 2011-11-03
Also published as: CN102395759A; JPWO2011135779A1; US20120131949A1

Abstract

Disclosed is a fluid machine (8A) provided with an expander (4) having an expander suction hole (4a) and an expander discharge hole (4b), a compressor (6) having a compressor suction hole (6a) and a compressor discharge hole (6b), and a shaft (81) for coupling the expander (4) to the compressor (6). The expander suction hole (4a) and the compressor suction hole (6a) are opened or closed in accordance with the rotation of the shaft (81). The expander suction hole (4a) is open when the compressor suction hole (6a) is closed. The compressor suction hole (6a) is open and does not communicate with the compressor discharge hole (6b) when the expander suction hole (4a) is closed.

Description

Fluid machinery and refrigeration cycle equipment

The present invention relates to a fluid machine used for a water heater or an air conditioner, and a refrigeration cycle apparatus using the fluid machine.

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

As shown in FIG. 12, in the fluid machine 100, the expander 110 and the compressor 120 are connected by a shaft 101. Both the expander 110 and the compressor 120 are rotary types, 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 that fits with the first eccentric portion 102 of the shaft 101, and an expander cylinder 111 that houses the expander piston 112. 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 partitioned into an intake side and a discharge side by an expander partition member 114. The expander partition member 114 is integrated with the expander piston 112, and the expander cylinder 111 is rotatably provided with a columnar shoe 117 that reciprocally supports the expander partition member 114. That is, the expander piston 112 swings while changing the distance from the fulcrum with the center of the shoe 117 as a fulcrum.

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

As shown in FIG. 14, the compressor 120 includes a compressor piston 122 that is configured by a roller bearing and is fitted to the second eccentric portion 103 of the shaft 101, and a compressor cylinder 121 that houses the compressor piston 122. Have. 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 partition member 114 is pressed against the compressor piston 122 by a spring.

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

Further, Patent Document 1 discloses a refrigeration cycle apparatus 200 shown in FIG. 15 constructed using the fluid machine 100 described above. The refrigeration cycle apparatus 200 preliminarily boosts the working fluid sucked into the main compressor 210 by the compressor 120 of the fluid machine 100, and includes the main compressor 210, the radiator 220, the expander 110, and the evaporator. 230 and the compressor 120 are connected by the flow path in this order, and the working fluid circuit is comprised.

JP 2004-324595 A

The fluid machine 100 is not provided with a driving means such as a motor, and is assumed to start up independently by the pressure of the working fluid in the refrigeration cycle apparatus 200 as shown in FIG. That is, by starting the main compressor 210, a high-pressure working fluid is caused to flow 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 this differential pressure to start the fluid machine 100.

However, when the fluid machine 100 is stopped in a state where the suction hole 110a of the expander 110 is closed, a high-pressure working fluid cannot flow into the expander working chamber 113, and torque that rotates the shaft 101. Does not occur.

On the other hand, prior to the present invention, the inventors of the present invention lead high-pressure working fluid discharged from the main compressor at the time of start-up to the compressor of the fluid machine, and give torque to the shaft also in the compressor. I figured out that. In other words, a bypass path is provided to connect the high pressure flow path between the main compressor and the radiator or between the radiator and the expander and the low pressure flow path between the evaporator and the compressor so that the compressor operates at startup. By causing high-pressure working fluid to flow also into the suction side of the chamber, a differential pressure is generated between the suction side and the discharge side of the compressor working chamber. Thereby, torque can be given to the shaft also in the compressor.

However, even if the above technique is applied to the fluid machine 100 disclosed in Patent Document 1, torque for rotating the shaft 101 may not be generated. The reason is as follows.

In the fluid machine 100 disclosed in Patent Document 1, the position of the expander partition member 114 and the position of the compressor partition member 124 coincide with each other 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 first eccentric portion 102. 2 The eccentric direction of the eccentric part 103 is shifted by 180 °. Further, in the compressor 120, the suction hole 120a communicates with the discharge hole 120b through the compressor working chamber 123 until the sliding point of the compressor piston 121 passes through the discharge hole 120b and reaches the suction hole 120a. .

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 expansion angle of the shaft 101 from 0 ° to about 140 ° is the expander working chamber 113. The working fluid can flow into the suction side. On the other hand, in the compressor 120, the suction hole 120a of the compressor 120 is closed by the compressor piston 122 when the rotation angle of the shaft 101 is about 190 ° to about 200 °, but the other side is the suction side of the compressor working chamber 123. The working fluid can flow in.

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 the torque that rotates the shaft 110 in both the expander 110 and the compressor 120. Cannot be generated. Further, as described above, the suction hole 120a is compressed from about 180 ° when the sliding point of the compressor piston 121 passes through the discharge hole 120b to about 190 ° when it reaches the suction hole 120a. The working fluid that communicates with the discharge hole 120b through the machine working chamber 123 and flows into the compressor working chamber 123 through 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 is stopped in a state where the rotation angle of the shaft is between about 180 ° and about 200 °, a torque for rotating the shaft 101 cannot be generated due to the pressure of the working fluid. The machine 100 cannot be activated independently.

In view of such circumstances, the present invention provides a fluid machine that can be activated independently by the pressure of a working fluid even when stopped in any state, and a refrigeration cycle apparatus using the fluid machine. With the goal.

In order to solve the above problems, the present invention expands the working fluid sucked from the expander suction hole and discharges it from the expander discharge hole, thereby recovering power from the working fluid, and a compressor suction hole. A compressor that boosts the working fluid sucked from the compressor and discharges the fluid from the compressor discharge hole; and the expander and the compressor are connected so that the compressor is driven by the power recovered by the expander A shaft, and the expander suction hole and the compressor suction hole are opened and closed as the shaft rotates, and the expander suction hole is open during a period in which the compressor suction hole is closed. And the fluid suction machine is maintained in a state in which the compressor suction hole is opened and is not in communication with the compressor discharge hole during a period in which the expander suction hole is closed.

The present invention is also a refrigeration cycle apparatus using the fluid machine described above, wherein a main compressor that compresses the working fluid, a radiator that dissipates the compressed working fluid, and the working fluid that has flowed out of the radiator expands. A working fluid circuit that circulates the working fluid, comprising: the expander that causes the working fluid to evaporate; and the compressor that pressurizes the working fluid that has flowed out of the evaporator and supplies the working fluid to the main compressor. A portion between the main compressor and the radiator or a portion between the radiator and the expander and a portion between the evaporator and the compressor in the working fluid circuit. A refrigeration cycle apparatus comprising a bypass path.

According to the above configuration, 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 flowing working fluid is compressed in the compressor working chamber. Since it is prevented from being discharged from the machine discharge hole, the fluid machine can be independently activated by the pressure of the working fluid, regardless of the state in which the fluid machine is stopped.

The block diagram of the refrigerating-cycle apparatus using the fluid machine which concerns on 1st Embodiment of this invention. The longitudinal cross-sectional view of the fluid machine which concerns on 1st Embodiment of this invention Sectional view along line III-III in Fig. 2 Sectional view taken along line IV-IV in FIG. Sectional view taken along line VV in FIG. 6A to 6C are operation principle diagrams of the fluid machine according to the first embodiment of the present invention. 7A to 7C are operation principle diagrams of the fluid machine according to the first embodiment of the present invention. The longitudinal cross-sectional view of the fluid machine which concerns on 2nd Embodiment of this invention IX-IX sectional view of FIG. 10A to 10C are operation principle diagrams of the fluid machine according to the second embodiment of the present invention. 11A to 11C are operation principle diagrams of the fluid machine according to the second embodiment of the present invention. Vertical section of a conventional fluid machine AA line sectional view of FIG. BB sectional view of FIG. Configuration diagram of a refrigeration cycle using the fluid machine of FIG.

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

(First embodiment)
<Configuration of refrigeration cycle apparatus>
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. The refrigeration cycle apparatus 1 includes a working fluid circuit 7 that circulates 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 a sub compressor, and these 2 to 6 are first to fifth channels (pipes). 7a to 7e are connected in this order. As the working fluid, for example, carbon dioxide or alternative chlorofluorocarbon can be used.

The main compressor 2 has a compression mechanism part 2a and a motor 2b for driving the compression mechanism part 2a in one sealed container 2c storing lubricating oil, and compresses the 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 radiates and cools the high-temperature and high-pressure working fluid compressed by the main compressor 2. 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 that has flowed out of the radiator 3, converts the expansion energy of the working fluid into mechanical energy, and thereby recovers power from the working fluid. In the present embodiment, the expander 4 is a rotary expander (details will be described later). The discharge port of the expander 4 is connected to the inlet of the evaporator 5 through the third flow path 7c.

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

The compressor 6 preliminarily boosts the medium-temperature and low-pressure working fluid flowing out from the evaporator 5 and supplies it to the main compressor 2. In the present embodiment, the compressor 6 is 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 through the fifth flow path 7e.

The expander 4 and the compressor 6 are arranged in one sealed container 80 in which lubricating oil is stored while being connected to each other by a shaft 81, and constitute a fluid machine 8A. In other words, the power recovered by the expander 4 is transmitted to the compressor 6 via the shaft 81, thereby driving the compressor 6.

Further, the refrigeration cycle apparatus 1 shown in FIG. 1 bypasses the first bypass passage 91 having both ends connected to the working fluid circuit 7 so as to bypass the evaporator 5 and the compressor 6, and the expander 4 and the evaporator 5. Thus, a second bypass passage (corresponding to the bypass passage of the present invention) 93 having both ends connected to the working fluid circuit 7 is provided. The first bypass passage 91 is provided with a first bypass valve 92 that controls the flow of the working fluid in the first bypass passage 91. The second bypass passage 93 has a working fluid flow in the second bypass passage 93. A second bypass valve 94 for controlling the above is provided.

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

The first bypass valve 92 operates when the pressure of the working fluid on the downstream side (outlet side) of the first bypass passage 91 is lower than the pressure of the upstream side (inlet side) working fluid. Allows the first bypass passage 91 to flow, and vice versa, the working fluid disables the first bypass passage 91 from flowing. 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 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 flow path (the third flow path 7c, the evaporator 5, the fourth flow path 7d) is lower, the working fluid passes through the first bypass path 91 from the third flow path 7c. 5 flows into the flow path 7e.

The second bypass path 93 is a second flow path 7b that guides the working fluid from the outlet of the radiator 3 to the suction port of the expander 4, and a fourth that guides the working fluid from the outlet of the evaporator 5 to the suction port of the compressor 6. It communicates with the flow path 7d. That is, the second bypass passage 93 is a passage through which the high-pressure working fluid flowing out from the radiator 3 can be directly sucked into the compressor 6 by bypassing the expander 4 and the evaporator 5. In the present embodiment, an on-off valve is used as the second bypass valve 94. However, the second bypass valve 94 is not limited to this, and a three-way valve may be used. Further, the second bypass path 92 may be a flow path that allows the high pressure working fluid to be directly sucked into the compressor 6, and the second bypass path 92 is configured to guide the working fluid from the discharge port of the main compressor 2 to the inlet of the radiator 3. The 1 flow path 7a and the 4th flow path 7d may be connected.

The second bypass valve 94 is opened during start-up control, so that the high-pressure working fluid that has flowed out of the radiator 3 passes from the second flow path 7b to the fourth flow path 7d via the second bypass path 93. Flows in.

In the refrigeration cycle apparatus 1 shown in FIG. 1, the working fluid flows in the fourth flow path 7d between the outlet of the evaporator 5 and the downstream end of the second bypass path 93 in the fourth flow path 7d. A compressor upstream valve 71 for controlling the compressor is provided. In the present embodiment, an on-off valve is used as the compressor upstream valve 71. The compressor upstream valve 71 is closed during start-up control, so that the working fluid flows from the evaporator 5 to the compressor 6, and the working fluid that has flowed into the fourth flow path 7 d through the second bypass passage 93. The flow to the evaporator 5 is prevented.

The second bypass valve 94 and the compressor upstream valve 71 are controlled by a control device (not shown). Although not shown, the refrigeration cycle apparatus 1 is provided with start detection means for detecting that the compressor 6 has started up. When the compressor 6 starts up, the start detection means switches from the start detection means to the control device. A detection signal is transmitted. As such activation detection means, for example, a method of providing a thermocouple in the third flow path 7c on the discharge side of the expander 4 and measuring the temperature of the working fluid in the third flow path 7c 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 apparatus 1, the pressure of the working fluid in the working fluid circuit 7 is substantially uniform when in an operation standby state (when stopped).

In the start control, first, the second bypass valve 94 is opened and the compressor upstream valve 71 is closed. As a result, 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. Subsequently, the main compressor 2 is started, and the working fluid in the fifth flow path 7e and the working fluid in the first bypass path 91 on the downstream side of the first bypass valve 92 are sucked into the main compressor 2. The

When suction of the working fluid into the main compressor 2 is started, the pressure of the working fluid in the fifth flow path 7e and the working fluid in the first bypass path 91 on the downstream side of the first bypass valve 92 decreases. To do. As a result, the first bypass valve 92, which is a check valve, is opened, and a flow path from the discharge port of the expander 4 to the compressor upstream valve 71 (the third flow path 7c, the evaporator) is opened in the first bypass path 91. 5, part of the fourth flow path 7d) flows in. 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 9 and the working fluid in the fifth flow path 7e. Then, it is compressed and discharged to the first flow path 7a. As a result, the pressure of the working fluid in the first bypass passage 91 upstream from the first bypass valve 92 and the working fluid in the flow path from the discharge port of the expander 4 to the compressor upstream valve 71 are also reduced.

On the other hand, the working fluid sucked into the main compressor 2 is compressed and discharged, whereby a flow path from the discharge port of the main compressor 2 to the suction port of the expander 4 (first flow path 7a, radiator 3). The pressure of the working fluid in the second flow path 7b) increases. Further, at the time of starting control, since the second bypass valve 94 is opened and the compressor upstream valve 71 is closed, the working fluid in the flow path from the discharge port of the main compressor 2 to the suction port of the expander 4 is Through the second bypass passage 93, the fluid also flows into the portion between the compressor upstream valve 71 and the suction port of the compressor 6 in the fourth flow path 7 d. Thereby, the pressure of the working fluid in the flow path (a part of the fourth flow path 7d) from the compressor upstream valve 71 to the suction port of the compressor 6 increases.

Therefore, between the working fluid (high pressure) in the suction side channel (second channel 7b) of the expander 4 and the working fluid (low pressure) in the discharge side channel (third channel 7c), and , Between the working fluid (high pressure) in the suction side channel (a part of the fourth channel 7d) and the working fluid (low pressure) in the discharge side channel (fifth channel 7e) of the compressor 6 Each has a high and low pressure difference. The high and low pressure differences of the working fluid act on the expander 4 and the compressor 6, respectively, and the fluid machine 8A can be easily activated independently.

When it is detected by the activation detection means described above that the compressor 6 has been activated, 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 apparatus 1 ends the start control, and shifts to a steady operation in which the working fluid is circulated through 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 path 93 on the downstream side of the second bypass valve 94 are sucked into the compressor 6 to be pressurized, and the fifth flow path 7e is discharged. Thereby, 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 changed from the discharge port of the expander 4 to the compressor 6. Pressure of the working fluid in the flow path (the third flow path 7c, the evaporator 5 and the fourth flow path 7d) to the suction port of the gas and the operation in the first bypass path 91 upstream of the first bypass valve 92. The pressure of the fluid becomes higher, and the first bypass valve 92 that is a check valve is closed. During steady operation, the pressure of the working fluid in the fifth flow path 7e and the working fluid in the first bypass path 91 on the downstream side of the first bypass valve 92 is high as described above. The bypass valve 92 maintains a closed state. As a result, the working fluid in steady operation circulates through the working fluid circuit 7.

<Configuration of fluid machinery>
Next, the configuration 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 sectional views of the fluid machine 8A corresponding to the lines III-III to VV in FIG. 3 to 5, the sealed container 80 is omitted.

The fluid machine 8A is a power recovery system in which the expander 4 and the compressor 6 are connected by the shaft 81 so that the compressor 6 is driven by the power recovered by the expander 4 as described above. In the present embodiment, the shaft 81 extends in the vertical direction, the expander 4 is disposed in the lower part in the sealed container 80, and the compressor 6 is disposed in the upper part in the sealed container 80. However, the positional relationship between the expander 4 and the compressor 6 may be reversed upside down, the shaft 81 may extend in the horizontal direction, and the expander 4 and the compressor 6 may be arranged in the horizontal direction. . Further, the sealed container 80 is filled with lubricating oil to such an extent that the oil level is located above the compressor 6.

1) Shaft The shaft 81 includes a first eccentric portion 81b for the expander 4 and a second eccentric portion 81c for the compressor 6 as an eccentric portion having a central axis at a position away from the axis of the shaft 81. Have. The shaft 81 is formed with an oil supply passage 81a that penetrates the shaft 81 in the axial direction and opens to the outer peripheral surface of the first eccentric portion 81b and the outer peripheral surface of the second eccentric portion 81c. The lubricating oil in the sealed container 80 is supplied to the sliding portions of the expander 4 and the compressor 6 through the oil supply passage 81a.

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

Specifically, as shown in FIG. 4, the expander 4 includes an expander piston 42 that fits with the first eccentric portion 81 b of the shaft 81, and an expander cylinder 41 that houses the expander piston 42. Yes. The expander cylinder 41 has an inner peripheral surface that forms a cylindrical surface whose central axis coincides with the axis of the shaft 81, and the expander piston 42 is disposed inside the expander cylinder 41 as the shaft 81 rotates. Eccentric rotation along the circumference. 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 partitioned by an expander partition member 44 into a suction side 43a and a discharge side 43b. An expander suction hole 4a is opened in a portion adjacent to the expander partition member 44 on the suction side 43a, and an expander discharge hole 4b is opened in a portion adjacent to the expander partition member 44 on the discharge side 43b. Yes.

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 into the expander working chamber 43 on a straight line passing through the axis of the shaft 81. Between the bottom of the groove 41a and the expander partition member 44, an urging means 45 that presses the expander partition member 44 against the outer peripheral surface of the expander piston 42 is disposed.

The biasing means 45 can be constituted by a compression coil spring, for example. Further, the urging means 45 may be a so-called gas spring or the like in which the back space between the rear end of the expander partition member 44 and the bottom of the groove 41a is a sealed space. Of course, the biasing means 45 may be constituted by a plurality of types of springs such as a compression coil spring and a gas spring. Note that the expander piston 42 and the expander partition member 44 may be integrated, and the biasing means 45 may not be provided.

Further, as shown in FIG. 2, the expander 4 includes a first closing member (inner closing member) 49 that closes the expander working chamber 43 from the compressor 6 side, and the expander working chamber 43 opposite to the compressor 6. It has a second closing member (outer closing member) 46 that is closed from the side, and a bearing member 47 that is disposed below the second closing member 46.

The bearing member 47 is fixed to the inner peripheral surface of the sealed container 80 and supports the lower portion of the shaft 81 to be rotatable. 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. A suction pipe 82 and a discharge pipe 83 that pass through the sealed container 80 are connected to the bearing member 47.

Both the first closing member 49 and the second closing member 46 have a flat disk shape in the axial direction of the shaft 81, and the shaft 81 passes through the center thereof. In the present embodiment, the second closing member 46 is provided with the expander suction hole 4a, and the first closing member 49 and the expander cylinder 41 are provided with the expander discharge hole 4b.

A circular recess 46a whose center coincides with the axis of the shaft 81 is provided on the lower surface of the second closing member 46, and the expander suction hole 4a extends from the upper surface of the second closing member 46 to the bottom surface of the recess 46a. The second closing member 46 is penetrated in the axial direction of the shaft 81 so as to extend straight. The expander suction hole 4 a communicates with the suction pipe 82 through a suction space in the recess 46 a and a suction path 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 sucked into the expander working chamber 43 from the expander suction hole 4a through the suction pipe 82, the suction path 47a, and the suction space in the recess 46a. Guided to side 43a.

On the other hand, as shown in FIG. 4, the expander discharge hole 4 b includes a vertical groove 41 b that is formed on the inner peripheral surface of the expander cylinder 41 and that is recessed radially outward, and a vertical groove on the lower surface of the first closing member 49. 41b and a lateral groove 49a formed so as to extend radially outward from a corresponding position. The outer end of the expander discharge hole 4 b communicates with the discharge pipe 83 via a discharge path 4 c formed so as to extend over 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 path 7c shown in FIG. 1 through the expander discharge hole 4b, the discharge path 4c, and the discharge pipe 83.

Furthermore, a rotating plate 48 is disposed in the recess 46a as a suction control mechanism that opens and closes the expander suction hole 4a 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 recess 46a.

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

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

The configuration of the expander 4 can be turned upside down. That is, the first closing member 49, the expander cylinder 41, the second closing member 46, the rotating plate 48, and the bearing member so that the first closing member 49 becomes the outer closing member and the second closing member 46 becomes the inner closing member. 47 may be arranged in this order from bottom to top. In this case, the shaft 81 may be loosely fitted to the bearing member 47, and the first closing member 49 may have a function of rotatably supporting the lower portion of the shaft 81.

3) Compressor As described above, in the present embodiment, the compressor 6 is a rotary compressor. The compressor 6 pressurizes the working fluid sucked from the compressor suction hole 6a and discharges it from the compressor discharge hole 6b.

Specifically, as shown in FIG. 5, the compressor 6 includes a compressor piston 62 that fits with the second eccentric portion 81 c of the shaft 81, and a compressor cylinder 61 that houses the compressor piston 62. Yes. The compressor cylinder 61 has an inner peripheral surface that forms a cylindrical surface whose central axis coincides with the axis of the shaft 81, and the compressor piston 62 is disposed inside the compressor cylinder 61 as the shaft 81 rotates. Eccentric rotation along the circumference. 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 63a and a discharge side 63b by a compressor partition member 64. A compressor suction hole 6a is opened in a portion adjacent to the compressor partition member 64 on the suction side 63a, and a compressor discharge hole 6b is opened in a portion adjacent to the compressor partition member 64 on the discharge side 63b. Yes.

The compressor partition member 64 has a plate shape and is reciprocally inserted into a groove 61 a provided in the compressor cylinder 61. The groove 61 a opens into the compressor working chamber 63 on a straight line passing through the axis of the shaft 81. Between the bottom of the groove 61 a and the compressor partition member 64, an urging means 65 that presses the compressor partition member 64 against the outer peripheral surface of the compressor piston 62 is disposed.

The biasing means 65 can be constituted by a compression coil spring, for example. Further, the biasing means 65 may be a so-called gas spring or the like in which a back space between the rear end of the compressor partition member 64 and the bottom of the groove 61a is a sealed space. Of course, the urging means 65 may be constituted by a plurality of types of springs such as a compression coil spring and a gas spring. The compressor piston 62 and the compressor partition member 64 may be integrated, and the urging unit 65 may not be provided.

As shown in FIG. 2, the compressor 6 includes a first closing member (inner closing member) 49 that closes the compressor working chamber 63 from the expander 4 side, and the compressor working chamber 63 opposite to the expander 4. It has a second closing member (outer closing member) 66 that is closed from the side, and a cover member 67 that is disposed above the second closing 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 have a 1st obstruction | occlusion member separately.

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. A suction pipe 84 that penetrates the sealed container 80 is connected to the compressor cylinder 61, and a discharge pipe 85 that penetrates the sealed container 80 is connected to the second closing member 66.

The second closing member 66 has a flat disk shape in the axial direction of the shaft 81, and the shaft 81 passes through the center thereof. The cover member 67 also has a flat disk shape in the axial direction of the shaft 81, and an opening for exposing the upper end portion of the shaft 81 is provided at the center thereof. In the present embodiment, the compressor cylinder 61 is provided with a compressor suction hole 6a, and the second closing member 66 is provided with a compressor discharge hole 6b.

The compressor suction hole 6 a penetrates the compressor cylinder 61 sideways, 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 low-pressure (high pressure during start-up control) working fluid from the fourth flow path 7d shown in FIG. 1 is guided from the compressor suction hole 6a to the suction side 63a of the compressor working chamber 63 via the suction pipe 84. .

Since the compressor suction hole 6a is opened 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 in other words only 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. 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 rotated only while the compressor piston 62 rotates about 5 ° to about 15 °. Closed by. Since the inner peripheral surface of the compressor cylinder 61 and the outer peripheral surface of the compressor piston 62 have different diameters, the compressor suction hole 6a is not completely closed by the compressor piston 62. In the specification, it is defined that the compressor suction hole 6a is closed while the sliding point of the compressor piston 62 is positioned on the compressor suction hole 6a as described above.

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

In the present embodiment, since the compressor discharge hole 6b is disposed at a position crossing the inner peripheral surface of the compressor cylinder 61, only when the sliding point of the compressor piston 62 is positioned on the compressor discharge hole 6b. In other words, the compressor discharge hole 6b is closed by the compressor piston 62 only while the compressor piston 62 rotates from about 345 ° to about 355 ° when the top dead center is 0 °. Note that, like the compressor suction hole 6a, the compressor discharge hole 6b is not strictly closed by the compressor piston 62, but in the present specification, as described above, the sliding of the compressor piston 62 is not performed. It is defined that the compressor discharge hole 6b is closed while the point is positioned on the compressor discharge hole 6b.

Also, a discharge valve 68 that automatically opens and closes the compressor discharge hole 6b by the pressure on the discharge side 63b of the compressor working chamber 63 by elastic deformation is disposed in the discharge chamber 66a.

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

The configuration of the compressor 6 can be turned upside down. That is, the cover member 67, the second closing member 66, the compressor cylinder 61, and the first closing member 49 are arranged from below so that the first closing member 49 becomes the outer closing member and the second closing member 66 becomes the inner closing member. You may arrange in this order on the top. In this case, the shaft 81 may be loosely fitted to the second closing member 66, and the first closing member 49 may have a function of rotatably supporting the upper portion of the shaft 81.

4) Reciprocal relationship The fluid machine 8A is in a state in which the expander suction hole 6a is open during the period when the compressor suction hole 6a is closed, and the compressor suction hole 6a is closed during the period when the expander suction hole 6a is closed. It is configured to be in an open state and maintained in a state not communicating with the compressor discharge hole 6b. 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 within a period during which the expander suction hole 6a is opened.

In order to realize this, the phase difference in the eccentric direction of the second eccentric portion 81c with respect to the eccentric direction of the first eccentric portion 81b when the rotation direction of the shaft 81 is positive is set to βc (where −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 (where −180 ° <βc ≦ 180 °), and the shaft of the shaft during the period when the expander suction hole 6a is opened When the rotation angle is θo, it is preferable that the following expression 1 is satisfied.
0.25θo ≦ βv−βc ≦ 0.75θo (Formula 1)

In the present embodiment, as shown in FIGS. 4 and 5, the position of the expander partition member 44 and the position of the compressor partition member 64 coincide with each other in the axial direction of the shaft 81, and the eccentricity of the second eccentric portion 81c. The direction is shifted by −90 ° with respect to the eccentric direction of the first eccentric portion 81b. That is, βc = −90 °, βv = 0 °, and βv−βc = 90 °. Further, θo = about 140 ° due to the shape of the rotating plate 48 as described above. Therefore, 0.25θo≈35 ° and 0.75θo≈105 °, which satisfies Expression 1.

The present invention is not limited to this. For example, the first eccentric portion 81b and the second eccentric portion 81c are eccentric in the same direction, and the position of the expander partition member 44 and the compressor partition member 64 are The position may be deviated within a range satisfying Expression 1, or both the eccentric direction and the position of the partition member may be deviated within a range satisfying Expression 1.

<Operation of fluid machinery>
Next, the operation of the fluid machine 8A during steady operation will be described with reference to FIGS. 6A to 6C and FIGS. 7A to 7C. In these drawings, the rotation angle θ of the shaft 81 when the expander piston 42 is located at the top dead center is 0 °.

First, the operation of the expander 4 will be described. As shown in FIGS. 6A to 6C, the shaft 81 rotates from θ = 0 °, and the rotating plate 48 rotates in synchronization therewith, whereby the expander suction hole 4a begins to be exposed from the rotating plate 48, and the expander suction The hole 4a is opened. 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. Thereafter, when the shaft 81 rotates about 30 °, the expander suction hole 4a is completely exposed. On the other hand, as shown in FIGS. 7A and 7B, when the shaft 81 rotates about 125 °, the expander suction hole 4a begins to be shielded by the rotating plate 48, and when the shaft 81 rotates about 140 °, the expander suction hole 4a. Is completely shielded, and the expander suction hole 4a is closed. Thereby, the suction stroke is completed.

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

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

As shown in FIG. 6C and FIG. 7A, when the shaft 81 rotates about 105 °, the compressor suction hole 6a is opened, and from the evaporator 5 through the compressor suction hole 6a to the suction side 63a of the compressor suction working chamber 63. Of low pressure working fluid. Then, after the compressor piston 62 further rotates and the suction side 63a of the compressor suction working chamber 63 communicates with the compressor discharge hole 6b, the compressor piston 62 passes through the top dead center, thereby causing the compressor working chamber 63 to pass. When the suction side 63a of the compressor moves to the discharge side 63b, the volume of the discharge side 63b of the compressor suction working chamber 63 gradually decreases as the shaft 81 rotates. Thereby, the working fluid in the discharge side 63b of the compressor suction working chamber 63 is compressed and pressurized. When the pressure of the working fluid in the discharge side 63b of the compressor suction 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 pushes and opens the discharge valve 68, and the compressor It discharges toward the main compressor 2 through the discharge hole 6b.

<Operation and effect of this embodiment>
In the present embodiment, as described above, the period during which the expander suction hole 4a is opened is θ = 0 ° to about 140 °, and the period during which the expander suction hole 4a is closed is θ = about 140 ° to 360 °. is there. On the other hand, the period during which the compressor suction hole 6a is closed is θ = about 95 ° to about 105 °, and the periods during which the compressor suction hole 6a is opened are θ = 0 ° to about 95 ° and θ = about 105 to 360 °. It is. The period during which the compressor discharge hole 6b communicates with the compressor discharge hole 6b through the compressor working chamber 63 is θ = about 85 ° to about 95 °. That is, after the compressor suction hole 6a communicates with the suction side 63a of the compressor working chamber 63, the expander suction hole 4a is closed, and before the suction side 63a of the compressor working chamber 63 communicates with the compressor discharge hole 6b. The expander suction hole 4a is opened.

As described in the section <Operation of refrigeration cycle apparatus>, when the refrigeration cycle apparatus 1 is started, the main compressor 2 is started with the second bypass valve 94 opened and the compressor upstream valve 71 closed. Therefore, the working fluid in the suction side channel of the expander 4 and the working fluid in the discharge side channel, and the working fluid and outlet side flow in the suction side channel of the compressor 6 are arranged. A high and low pressure difference is generated between the working fluid in the passage. In other words, the upstream flow path of the expander suction hole 4a through the suction pipe 82 of the fluid machine 8A and the upstream flow path of the compressor suction hole 6a 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, the expansion machine suction hole 4a or the shaft 81 of the fluid machine 8A is in any angular position when the refrigeration cycle apparatus 1 is started. At least one of the compressor suction holes 6a is always open, and a high-pressure working fluid always flows into at least one of the suction side 43a of the expander working chamber 43 or the suction side 63a of the compressor working chamber 63. To do. The compressor suction hole 6a communicates with the compressor discharge hole 63b through the compressor working chamber 63 after the expander suction hole 4a is opened. Therefore, even if the fluid machine 8A is stopped in any state, it is possible to generate a torque for rotating the shaft 81 by one or both of the expander 4 and the compressor 6, and start up independently by the pressure of the working fluid. be able to.

Specifically, when the shaft 81 is located within a range of θ = 0 ° to about 85 °, both the expander suction hole 4a and the compressor suction hole 6a are opened, and the expander working chamber 43 Since the high-pressure working fluid flows into the suction side 43 a and the suction side 63 a of the compressor working chamber 63, torque is generated in the expander 4 and the compressor 6.

When the shaft 81 is positioned within the range of θ = about 85 ° to about 95 °, the compressor suction hole 6a is open, but communicates with the compressor discharge hole 6b through the compressor working chamber 63. In addition, since the working fluid blows out from the compressor suction hole 6a to the compressor discharge hole 26b, no torque is generated in the compressor 6. However, since the expander suction hole 4 a is open and high-pressure working fluid flows into the suction side of the expander working chamber 63, torque is generated in the expander 4.

When the shaft 81 is positioned within the range of θ = about 95 ° to 105 °, the compressor suction hole 6a is closed and no torque is generated in the compressor 6, but the expander suction hole 4a is opened. The high pressure working fluid flows into the suction side 63 a of the compressor working chamber 63, so that torque is generated in the compressor 6.

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

When the shaft 81 is positioned within the range of θ = about 140 ° to 360 °, the expander suction hole 4a is closed and no torque is generated in the expander 4, but the compressor suction hole 6a is opened. The high pressure working fluid flows into the suction side 63 a of the compressor working chamber 63, so that torque is generated in the compressor 6.

Thus, in the present embodiment, when the refrigeration cycle apparatus 1 is started, the fluid machine 8A that does not have a drive device can be reliably started only by the pressure of the working fluid, and the reliability of the refrigeration cycle apparatus 1 can be improved. 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. In the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted. Moreover, since the refrigerating cycle apparatus using the fluid machine 8B is the same as the refrigerating cycle apparatus 1 shown in FIG. 1, the description is also abbreviate | omitted.

<Configuration of fluid machinery>
The fluid machine 8B of the present embodiment is different from the fluid machine 8A of the first embodiment in that the suction pipe 84 is connected to the second closing member 66, and the compressor 6 has a discharge valve 68 (see FIG. 2). Is a fluid pressure motor type compressor. That is, the compressor 6 pressurizes the working fluid without changing the volume of the working fluid.

Specifically, the second closing member 66 is provided with the compressor suction hole 6 a exposed only on the suction side 63 a of the compressor working chamber 63, and the compressor discharge hole 6 b is provided with the compressor working chamber 63. It is provided so as to be exposed only to the discharge side 63b. Both the compressor suction hole 6 a and the compressor discharge hole 6 b extend in the axial direction of the shaft 81. The second closing member 66 includes a suction path 6c that communicates the upper end of the compressor suction hole 6a and the suction pipe 84, and a discharge path 6d that communicates the upper end of the compressor discharge hole 6b and the discharge pipe 85. Is formed.

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 gradually separate from the inner peripheral surface of the compressor cylinder 61. The outer side of the compressor suction hole 6a and the compressor discharge hole 6b (the side on the inner peripheral surface side of the compressor cylinder 61) is the outer periphery of the compressor piston 62 when the compressor piston 62 is located at the top dead center. It is formed in an arc shape that matches the surface. That is, the compressor suction hole 6a is completely closed by the compressor piston 63 only for a short period after the compressor piston 62 is located at the top dead center, and the compressor discharge hole 6b is closed by the compressor piston 62 at the top dead center. It is completely closed by the compressor piston 63 only for a short period before it is located at.

In the present embodiment, the relationship between the eccentric direction of the first eccentric portion 81b of the shaft 81 and the eccentric direction of the second eccentric portion 82b and the relationship between the position of the expander partition 44 and the position of the compressor partition member 64 are as follows: This is the same as in the first embodiment.

Note that the compressor suction hole 6 a and the compressor discharge hole 6 b are not necessarily provided in the second closing member 66, and either one or both of them may be provided in the first closing member 49.

<Operation of fluid machine 8B>
Next, the operation of the fluid machine 8A during steady operation will be described with reference to FIGS. 10A to 10C and FIGS. 11A to 11C. In these drawings, the rotation angle θ of the shaft 81 when the expander piston 42 is located at the top dead center is 0 °. Since the operation of the expander 4 is the same as that of the first embodiment, the description thereof is omitted.

10C and FIGS. 11A to 11C, the compressor suction hole 6a is completely closed by the compressor piston 62 until the shaft 81 rotates from 90 ° to about 95 °. After the shaft 81 rotates about 95 °, the compressor suction hole 6a is gradually opened, and the low-pressure working fluid from the evaporator 5 passes through the compressor suction hole 6a to the suction side 63a of the compressor suction working chamber 63. Inhaled. Thereafter, 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 rotates again to 90 °, the suction stroke is completed, and the suction side 63a of the compressor working chamber 63 shifts to the discharge side 63b. After the shaft 81 rotates 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. By pushing out the working fluid by the compressor piston 62, the working fluid is pressurized. The compressor discharge hole 63b is gradually closed after the shaft 81 rotates about 300 °, and is completely closed by the compressor piston 62 until the shaft 81 rotates about 85 ° to 90 °.

<Operation and effect of this embodiment>
In the present embodiment, as described above, the period during which the expander suction hole 4a is opened is θ = 0 ° to about 140 °, and the period during which the expander suction hole 4a is closed is θ = about 140 ° to 360 °. is there. On the other hand, the period during which the compressor suction hole 6a is closed is θ = 90 ° to about 95 °, and the periods during which the compressor suction hole 6a is opened are 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.

In the present embodiment, since the fluid machine 8A is configured as described above, the expansion machine suction hole 4a or the shaft 81 of the fluid machine 8A is in any angular position when the refrigeration cycle apparatus 1 is started. At least one of the compressor suction holes 6a is always open, and a high-pressure working fluid always flows into at least one of the suction side 43a of the expander working chamber 43 or the suction side 63a of the compressor working chamber 63. To do. Therefore, even if the fluid machine 8A is stopped in any state, it is possible to generate a torque for rotating the shaft 81 by one or both of the expander 4 and the compressor 6, and start up independently by the pressure of the working fluid. be able to.

Specifically, when the shaft 81 is positioned within the range of θ = 0 ° to 90 °, both the expander suction hole 4a and the compressor suction hole 6a are opened, and the suction of the expander working chamber 43 is performed. Since high-pressure working fluid flows into the side 43 a and the suction side 63 a of the compressor working chamber 63, torque is generated in the expander 4 and the compressor 6.

When the shaft 81 is located within the range of θ = 90 ° to about 95 °, the compressor suction hole 6a is closed and no torque is generated in the compressor 6, but the expander suction hole 4a is opened. The high pressure working fluid flows into the suction side 63 a of the compressor working chamber 63, so that torque is generated in the compressor 6.

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

(Other embodiments)
In the above embodiment, the suction plate control mechanism for opening and closing the expander suction hole 4a with the rotation of the shaft 81 is configured by the rotating plate 48, but the suction control mechanism of the present invention is not limited to this. Various types of structures can be employed. For example, an intake control mechanism having a structure disclosed in Patent Document 1 may be adopted, an arc groove is provided on the upper surface of the first eccentric portion 81 b of the shaft 81, and the arc groove is formed on the lower surface of the first closing member 49. A suction control mechanism provided with a communication groove that communicates the suction side with the suction side 43a of the expander working chamber 43 may be employed.

The present invention can surely realize the self-sustained activation of the fluid machine, and is particularly useful for a refrigeration cycle apparatus in which the fluid machine is used as a power recovery system.

Claims

An expander that recovers power from the working fluid by expanding the working fluid sucked from the expander suction hole and discharging it from the expander discharge hole;
A compressor that pressurizes the working fluid sucked from the compressor suction hole and discharges it 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 are opened and closed as the shaft rotates,
The period during which the compressor suction hole is closed is in the state in which the expander suction hole is opened, and the period in which the expander suction hole is closed is in the state in which the compressor suction hole is opened and the compression is performed. Maintained in a state not communicating with the machine discharge hole,
Fluid machinery.
The shaft has a first eccentric part for the expander and a second eccentric part for the compressor,
The compressor includes a compressor piston that fits into the second eccentric portion, a compressor cylinder that houses the compressor piston, and a compressor operation that is formed between the compressor piston and the compressor cylinder. A compressor partition member that partitions the chamber into a suction side and a discharge side,
Within the period when the expander suction hole is opened, the compressor piston slides on the inner peripheral surface of the compressor cylinder on the compressor piston so that the sliding point coincides with the compressor partition member. The fluid machine of claim 1, passing through a point.
The expander includes an expander piston that fits into the first eccentric portion, an expander cylinder that houses the expander piston, and an expander operation that is formed between the expander piston and the expander cylinder. An expander partition member that partitions the chamber into a suction side and a discharge side,
Βc (where −180 ° <βc ≦ 180 °) is the phase difference of the eccentric direction of the second eccentric portion with respect to the eccentric direction of the first eccentric portion when the rotation direction of the shaft is positive, and the expander partition The phase difference of the position of the compressor partition member relative to the position of the member is βv (where −180 ° <βc ≦ 180 °), and the rotation angle of the shaft during the period when the expander suction hole is opened is θo. sometimes,
The fluid machine according to claim 2, wherein 0.25θo ≦ βv−βc ≦ 0.75θo is satisfied.
The compressor suction hole is provided in the compressor cylinder and opens on an inner peripheral surface of the compressor cylinder,
The expander suction hole is closed after the compressor suction hole communicates with the suction side of the compressor working chamber, and the expander suction hole before the suction side of the compressor working chamber communicates with the compressor discharge hole. The fluid machine according to claim 2 or 3, wherein is opened.
The fluid machine according to claim 4, wherein the compressor further includes a discharge valve that opens and closes the compressor discharge hole by a pressure on a discharge side of the compressor working chamber.
The compressor further includes an inner closing member that closes the compressor working chamber from the expander side, and an outer closing member that closes the compressor working chamber from the opposite side of the expander,
The compressor suction hole is provided in the inner closing member or the outer closing member so as to be exposed only on the suction side of the compressor working chamber,
The expander suction hole is closed after the compressor suction hole communicates with the suction side of the compressor working chamber, and the expander suction hole is opened before the compressor suction hole is closed. 4. The fluid machine according to 3.
The fluid machine according to claim 6, wherein the compressor discharge hole is provided in the inner closing member or the outer closing member so as to be exposed only on a discharge side of the compressor working chamber.
The fluid machine according to claim 3, wherein the expander further includes a suction control mechanism that opens and closes the expander suction hole as the shaft rotates.
The expander further includes an inner closing member that closes the expander working chamber from the compressor side, and an outer closing member that closes the expander working chamber from the opposite side of the compressor,
The expander suction hole is provided in the inner closing member or the outer closing member so as to penetrate the inner closing member or the outer closing member,
The suction control mechanism has a large diameter that covers the expander suction hole that is attached to the shaft so as to rotate while being in contact with a surface of the inner closing member or the outer closing member opposite to the expander working chamber. The fluid machine according to claim 8, wherein the fluid machine is a rotating plate having a small-diameter portion exposing the expansion portion and the expander suction hole.
A refrigeration cycle apparatus using the fluid machine according to any one of claims 1 to 9,
From the main compressor that compresses the working fluid, the radiator that dissipates the compressed working fluid, the expander that expands the working fluid flowing out from the radiator, the evaporator that evaporates the expanded working fluid, and the evaporator A working fluid circuit that circulates the working fluid, including the compressor that boosts the flowing working fluid and supplies it to the main compressor;
A bypass in the working fluid circuit for communicating a portion between the main compressor and the radiator or a portion between the radiator and the expander and a portion between the evaporator and the compressor. Road,
A refrigeration cycle apparatus comprising: