WO2010073586A1 - Refrigeration cycle device - Google Patents
Refrigeration cycle device Download PDFInfo
- Publication number
- WO2010073586A1 WO2010073586A1 PCT/JP2009/007066 JP2009007066W WO2010073586A1 WO 2010073586 A1 WO2010073586 A1 WO 2010073586A1 JP 2009007066 W JP2009007066 W JP 2009007066W WO 2010073586 A1 WO2010073586 A1 WO 2010073586A1
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- WIPO (PCT)
- Prior art keywords
- compressor
- working fluid
- expander
- refrigeration cycle
- cycle apparatus
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0401—Refrigeration circuit bypassing means for the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/14—Power generation using energy from the expansion of the refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/01—Timing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/191—Pressures near an expansion valve
Definitions
- the present invention relates to a refrigeration cycle apparatus.
- a refrigeration cycle apparatus 500 shown in FIG. 9 is known as a refrigeration cycle apparatus including an expander that recovers power by expanding a working fluid and a second compressor that preliminarily boosts the working fluid.
- a refrigeration cycle apparatus 500 including an expander that recovers power by expanding a working fluid and a second compressor that preliminarily boosts the working fluid.
- the refrigeration cycle apparatus 500 includes a first compressor 1, a radiator 2, an expander 3, an evaporator 4, a second compressor 5, and a flow connecting these elements in this order.
- a working fluid circuit 6 formed by the passages 10a to 10e is provided.
- the second compressor 5 is connected to the expander 3 by a power recovery shaft 7 and is driven by receiving the mechanical energy recovered by the expander 3 via the power recovery shaft 7.
- bypass path 8 that bypasses the second compressor 5 and a bypass valve 9 that controls the flow of the working fluid in the bypass path 8 are provided.
- the upstream end of the bypass path 8 is connected to a flow path 10d that connects the outlet of the evaporator 4 and the suction port of the second compressor 5, and the downstream end of the bypass path 8 is connected to the discharge port of the second compressor 5 and the second outlet.
- Compressor 1 is connected to a flow path 10e connecting the suction port.
- the refrigeration cycle apparatus 500 is started according to the following procedure. First, the operation of the first compressor 1 is started and the bypass valve 9 is opened. As a result, the working fluid in the evaporator 4 is sucked into the first compressor 1 through the bypass 8 as indicated by the solid line arrow in FIG. 9. By increasing the pressure of the working fluid by the first compressor 1 and discharging it, the pressure at the suction port of the expander 3 increases. As a result, as shown in FIG. 10, a pressure difference is generated before and after the expander 3, and the expander 3 and the second compressor 5 can be started quickly.
- bypass valve 9 is closed, and the working fluid that has flowed out of the evaporator 4 is second compressed through the flow path 10d as indicated by a dashed line arrow in FIG. Inhaled by machine 5.
- the bypass path 8 it can shift to steady operation smoothly.
- the second compressor 5 is a load when starting the expander 3. That is, the friction between the component parts of the second compressor 5 and the power recovery shaft 7 becomes the drive resistance of the expander 3.
- the second compressor 5 and the expander 3 form a single-path working fluid circuit 6, and their rotational speed is a common power recovery. Since they are connected by the shaft 7, they are the same. Therefore, the volume of the second compressor 5 is set so that the mass of the working fluid to be sucked by the second compressor 5 per unit time is equal to the mass of the working fluid to be sucked by the expander 3 per unit time. And the volume of the expander 3 must be set.
- FIG. 11 is a Mollier diagram when carbon dioxide is used as a working fluid in a conventional refrigeration cycle apparatus 500.
- the pressure of the working fluid sucked by the second compressor 5 is 40 kg / cm 2 and its temperature is about 10 ° C. (in FIG. A)
- the density of the working fluid at this time is 108.0 kg / m 3 .
- the pressure of the working fluid sucked by the expander 3 is 100 kg / cm 2 , the temperature thereof is 40 ° C. (point C in FIG. 11), and the density of the working fluid at this time is 628.61 kg / m 3 .
- the suction volume (m 3 ) of the second compressor 5 is Vc
- the suction volume (m 3 ) of the expander 3 is Ve
- the rotational speed (S ⁇ 1 ) of the power recovery shaft 7 per second is N.
- the mass (kg / s) of the working fluid that can be sucked by the second compressor 5 per second and the mass (kg / s) of the working fluid that can be sucked by the expander 3 per second are expressed by (Equation 1), respectively. ) And (Formula 2).
- the expander 3 when the refrigeration cycle apparatus 500 is activated, the expander 3 must drive the second compressor 5 having a suction volume approximately 5.8 times that of the expander 3. Further, when the ratio between the density of the working fluid to be sucked by the second compressor 5 and the density of the working fluid to be sucked by the expander 3 becomes larger, the suction volume of the second compressor 5 and the expander 3 The ratio to the suction volume is also increased. That is, the suction volume of the expander 3 is smaller than the suction volume of the second compressor 5, and the drive resistance of the expander 3 when the second compressor 5 is started is relatively large. Therefore, depending on the operating conditions of the refrigeration cycle apparatus 500, the expander 3 may not be able to drive the second compressor 5 at the time of startup. Alternatively, in order to obtain a driving force necessary for driving the second compressor 5, it is necessary to apply an excessive pressure to the suction port side of the expander 3 as compared with the steady operation, which causes a problem in safety such as a pressure resistance. May occur.
- This invention solves the said conventional subject, and aims at providing the refrigerating-cycle apparatus which can be started stably reliably.
- the present invention A first compressor that compresses the working fluid; a radiator that dissipates heat from the working fluid compressed by the first compressor; an expander that recovers power from the working fluid by expanding the working fluid dissipated by the radiator; An evaporator that evaporates the working fluid expanded by the expander, a second compressor that pressurizes the working fluid evaporated by the evaporator and supplies the working fluid to the first compressor, and these elements are connected in this order.
- a working fluid circuit formed by a flow path;
- a power recovery shaft connecting the expander and the second compressor so that the second compressor is driven by the power recovered by the expander;
- a first bypass to communicate with, A first bypass valve that is provided in the first bypass passage and controls the flow of the working fluid in the first bypass passage;
- a refrigeration cycle apparatus is provided.
- a high-pressure working fluid equivalent to that supplied to the inlet of the expander can be supplied to the inlet of the second compressor at the time of startup.
- the pressure at the discharge port of the second compressor is the same as the suction port of the first compressor, that is, a relatively low pressure. That is, a large pressure difference can be generated before and after the second compressor. Therefore, the refrigeration cycle apparatus of the present invention can be reliably and stably started regardless of operating conditions.
- Configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention Flow chart of start-up control of the refrigeration cycle apparatus in Embodiment 1 of the present invention
- Flow chart of start control of the refrigeration cycle apparatus in Embodiment 2 of the present invention Configuration diagram of a refrigeration cycle apparatus according to Embodiment 3 of the present invention. Schematic which shows the state at the time of starting of the refrigerating cycle apparatus of Embodiment 1 and 2 Schematic which shows the state at the time of starting of the refrigerating-cycle apparatus in Embodiment 3.
- Configuration diagram of the refrigeration cycle system in the reference example Schematic showing the flow of working fluid at the time of startup of a conventional refrigeration cycle apparatus
- Schematic showing the flow of working fluid when starting the refrigeration cycle apparatus of Embodiment 1, Embodiment 2 and Reference Example Configuration diagram of conventional refrigeration cycle equipment
- Schematic which shows the state at the time of starting of the refrigerating cycle apparatus shown in FIG. Mollier diagram when carbon dioxide is used as working fluid in a conventional refrigeration cycle system
- FIG. 1 is a configuration diagram of a refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
- the refrigeration cycle apparatus 100 includes a first compressor 101, a radiator 102, an expander 103, an evaporator 104, and a second compressor 105 that are connected to flow paths (pipes) 106a to 106a.
- the working fluid circuit 106 is formed by connecting them sequentially by 106e.
- a refrigerant such as carbon dioxide can be used.
- the first compressor 101 is configured by disposing a compression mechanism unit 101a and a motor 101b for driving the compression mechanism unit 101a in one sealed container 101c storing lubricating oil, so that the working fluid is heated to a high temperature. Compress to high pressure.
- a scroll compressor or a rotary compressor can be used as the first compressor 101.
- the discharge port of the first compressor 101 is connected to the inlet of the radiator 102 via the flow path 106a.
- the heat radiator 102 radiates (cools) the high-temperature and high-pressure working fluid compressed by the first compressor 101.
- the outlet of the radiator 102 is connected to the inlet of the expander 103 via the flow path 106b.
- the expander 103 expands the medium-temperature and high-pressure working fluid that has flowed out of the radiator 102, converts the expansion energy (power) of the working fluid into mechanical energy, and collects it.
- the discharge port of the expander 103 is connected to the inlet of the evaporator 104 through the flow path 106c.
- a scroll expander or a rotary expander can be used as the expander 103.
- a fluid pressure motor type expander can be used as the expander 103.
- the fluid pressure motor type expander includes a process of sucking the working fluid from the radiator 102 and a process of discharging the sucked working fluid to the evaporator 104 without performing a substantial expansion process in the working chamber. This is a fluid machine that collects power from the working fluid.
- the detailed structure and operating principle of the fluid pressure motor type expander are disclosed in, for example, International Publication No. 2008/050654.
- the evaporator 104 heats and evaporates the low-temperature and low-pressure working fluid expanded by the expander 103.
- the outlet of the evaporator 104 is connected to the suction port of the second compressor 105 through the flow path 106d.
- the second compressor 105 sucks the medium-temperature and low-pressure working fluid that has flowed out of the evaporator 104, preliminarily increases the pressure, and then discharges it to the first compressor 101.
- the discharge port of the second compressor 105 is connected to the suction port of the first compressor 101 via a flow path 106e.
- a scroll compressor or a rotary compressor can be used as the second compressor 105.
- a fluid pressure motor type compressor can be used as the second compressor 105.
- the fluid pressure motor type compressor performs a process of sucking the working fluid from the evaporator 104 and a step of discharging the sucked working fluid to the first compressor 101, so that the working fluid is obtained. It is a fluid machine that boosts pressure.
- the fluid pressure motor type compressor means a fluid machine that does not substantially change the volume of the working fluid in the working chamber.
- the structure of the fluid pressure motor type compressor is basically the same as the structure of the fluid pressure motor type expander, and is disclosed in detail in the previous document.
- the expander 103 and the second compressor 105 are accommodated in a single sealed container 109 that stores lubricating oil.
- the expander 103 is connected to the second compressor 105 by a power recovery shaft 107.
- the expander 103, the second compressor 105, and the power recovery shaft 107 transmit the mechanical energy (power) recovered by the expander 103 to the second compressor 105 via the power recovery shaft 107, so that the second compressor It functions as a power recovery system 108 that drives 105.
- the second compressor 105 has a volume larger than that of the expander 103.
- the ratio (Vc / Ve) of the volume Vc of the second compressor 105 to the volume Ve of the expander 103 is set in the range of 5 to 15, for example.
- the ratio (Vc / Ve) tends to be large.
- the larger the ratio (Vc / Ve) the larger the driving force (torque) is required to start the power recovery system 108 independently.
- the “volume of the second compressor 105” means the confined volume, that is, the volume of the working chamber when the suction process is completed. The same applies to the expander 103.
- the refrigeration cycle apparatus 100 further includes a first bypass passage 112 and a first bypass valve 113.
- the first bypass path 112 connects a flow path 106 b that connects the outlet of the radiator 102 and the suction port of the expander 103, and a flow path 106 d that connects the outlet of the evaporator 104 and the suction port of the second compressor 105.
- the first bypass valve 113 is provided in the first bypass passage 112 and controls the flow of the working fluid in the first bypass passage 112.
- the upstream end K1 of the first bypass path 112 is connected to the flow path 106b, and the downstream end K2 of the first bypass path 112 is connected to the flow path 106d. That is, the first bypass passage 112 causes the second compressor 105 to directly suck the working fluid in the flow passage 106b bypassing the expander 103 and the evaporator 104 before the power recovery shaft 107 rotates. It is a flow path that can. *
- the position of the upstream end K1 is not limited to the position shown in FIG. 1 as long as the pressure at the suction port of the second compressor 105 can be increased when the refrigeration cycle apparatus 100 is started. That is, a part of the working fluid circuit 106 from the discharge port of the first compressor 101 to the suction port of the expander 103, and a part of the working fluid circuit 106 from the outlet of the evaporator 104 to the suction port of the second compressor 105 , The position of the upstream end K1 of the first bypass path 112 is not particularly limited.
- the first bypass path 112 connects the flow path 106 a connecting the discharge port of the first compressor 101 and the inlet of the radiator 102, and the outlet of the evaporator 104 and the suction port of the second compressor 105. It may be connected to the working fluid circuit 106 so as to communicate with the flow path 106d. In some cases, the first bypass path 112 may branch from the radiator 102. For example, in the case where the radiator 102 includes an upstream portion and a downstream portion, the first bypass path 112 can be easily branched from between the two portions.
- the first bypass valve 113 is provided at the upstream end of the first bypass passage 112.
- the "upstream end”, the part between the total length of the first bypass passage 112 when defining a L 1, and the upstream end K1, and L 1/4 advanced position towards the upstream end K1 to the downstream end K2 corresponds to.
- the position of the first bypass valve 113 is not particularly limited, and may be provided, for example, at the downstream end of the first bypass path 112.
- the “downstream end”, corresponds to the portion between the downstream end K2, and L 1/4 advanced position towards the downstream end K2 the upstream end K1.
- an on-off valve is used as the first bypass valve 113, but the present invention is not limited to this.
- a three-way valve can be used as the first bypass valve 113.
- the use of a three-way valve has the advantage of reducing the number of pipe connections.
- the refrigeration cycle apparatus 100 is between the outlet of the evaporator 104 and the inlet of the second compressor 105, and is closer to the evaporator 104 than the downstream end K ⁇ b> 2 of the first bypass path 112.
- the start assist valve 114 controls the flow of the working fluid in the flow path 106d.
- An opening / closing valve can be used as the activation assist valve 114.
- the working fluid in the flow path 106b can flow directly to the suction port of the second compressor 105 via the first bypass path 112. At that time, by closing the start assist valve 114, it is possible to prevent the working fluid from flowing from the evaporator 104 to the second compressor 105.
- the refrigeration cycle apparatus 100 further includes a second bypass passage 110 and a second bypass valve 111.
- the second bypass path 110 is a flow path 106 c that connects the discharge port of the expander 103 and the inlet of the evaporator 104, and a flow path 106 e that connects the discharge port of the second compressor 105 and the suction port of the first compressor 101. Is connected to the working fluid circuit 106. That is, the second bypass passage 110 bypasses the evaporator 104 and the second compressor 105.
- the second bypass valve 111 is provided in the second bypass passage 110 and controls the flow of the working fluid in the second bypass passage 110.
- the upstream end H1 of the second bypass path 110 is connected to the flow path 106c, and the downstream end H2 of the second bypass path 110 is connected to the flow path 106e. That is, the second bypass passage 110 is a passage through which the working fluid in the passage 106c can be directly sucked into the first compressor 101, bypassing the evaporator 104 and the second compressor 105.
- the position of the upstream end H1 is not limited to the position shown in FIG.
- the upstream end H ⁇ b> 1 may be located anywhere in the section from the discharge port of the expander 103 to the downstream end K ⁇ b> 2 of the first bypass path 112. That is, the second bypass path 110 includes a part of the working fluid circuit 106 (a part of the flow path 106d) from the outlet of the evaporator 104 to the downstream end K2 of the first bypass path 112, and a discharge port of the second compressor 105.
- the second bypass path 110 may branch from the evaporator 104.
- the second bypass passage 110 can be easily branched from between the two portions.
- the second bypass valve 111 is provided at the upstream end of the second bypass passage 110.
- the second bypass valve 111 may also be provided at the downstream end of the second bypass path 111.
- the "downstream end”, corresponds to a portion between the downstream end H2, and L 2/4 advanced position towards the downstream end H2 at the upstream end H1.
- a check valve is used as the second bypass valve 111.
- the present invention is not limited to this, and an on-off valve or a three-way valve may be used.
- the second bypass valve 111 allows the working fluid in the flow path 106c to flow to the second bypass path 110. That is, the pressure in the flow path 106e is lower than the pressure in the flow path (flow path 106c, evaporator 104, flow path 106d) between the discharge port of the expander 103 and the suction port of the second compressor 105. Sometimes, the working fluid in the flow path 106 c can flow directly to the suction port of the first compressor 101 via the second bypass passage 110.
- the refrigeration cycle apparatus 100 also includes a controller 117 that controls opening and closing of the first bypass valve 113 and the start assist valve 114.
- the first bypass valve 113 and the startup assist valve 114 are provided with valve opening / closing means 115 and 116, respectively.
- the valve opening / closing means 115 and 116 are typically composed of actuators such as solenoids for operating the valves, and are controlled by the controller 117.
- the controller 117 is typically composed of a microcomputer.
- An input device 118 provided with a start button is connected to the controller 117. When an operation command is input to the controller 117 through the input device 118, a predetermined control program stored in the internal memory of the controller 117 is executed.
- a start command (start signal) is sent from the input device 118 to the controller 117.
- the controller 117 executes predetermined start control described later with reference to FIG. 2 in response to obtaining the start command.
- the controller 117 also controls the operation of the motor 101b that operates the first compressor 101.
- the refrigeration cycle apparatus 100 includes an activation detector 119 for detecting that the second compressor 105 has been activated.
- the activation detector 119 transmits a detection signal to the controller 117.
- the controller 117 detects activation of the second compressor 105 based on obtaining the detection signal.
- a temperature detector, a pressure detector, or the like can be used as the activation detector 119.
- the activation detector 119 as a temperature detector includes a temperature detection element such as a thermocouple or a thermistor, for example, and the temperature of the working fluid to be sucked into the expander 103 and the working fluid discharged from the expander 103. A difference ⁇ T from the temperature is detected.
- the activation detector 119 as a pressure detector includes, for example, a piezoelectric element, and detects a difference ⁇ P between the pressure of the working fluid to be sucked into the expander 103 and the pressure of the working fluid discharged from the expander 103.
- a timer that measures the elapsed time from the start point of the first compressor 101 may be provided as the start detector 119 that detects the start of the second compressor 105.
- a timer can also be provided by the function of the controller 117.
- the controller 117 itself can serve as the activation detector 119.
- a contact-type or non-contact-type displacement sensor that detects driving of the power recovery shaft 107, for example, an encoder, may be provided as the activation detector 119 that detects activation of the second compressor 105.
- the method for detecting “the second compressor 105 has been activated” differs as follows.
- a predetermined value T 1 obtained experimentally or theoretically is set by the controller 117.
- the controller 117 detects that the second compressor 105 has been started when the temperature difference ⁇ T detected by the temperature detector is greater than a predetermined value T 1 .
- a predetermined value P 1 obtained experimentally or theoretically is set by the controller 117.
- the controller 117 detects that the second compressor 105 has been started when the pressure difference ⁇ P detected by the pressure detector is greater than a predetermined value P 1 .
- the reason why the activation of the second compressor 105 can be detected by comparing the temperature difference ⁇ T with the predetermined value T 1 or comparing the pressure difference ⁇ P with the predetermined value P 1 is as follows.
- the first compressor 101 When the first compressor 101 is activated, the working fluid discharged from the first compressor 101 is supplied to the suction port of the second compressor 105 through the first bypass passage 112.
- the power recovery system 108 is activated.
- the second compressor 105 serves as a drive source, the power recovery system 108 rotates before a large temperature difference occurs between the suction temperature of the first compressor 101 and the discharge temperature of the first compressor 101. start.
- the pressure difference of the refrigeration cycle apparatus 100 is not sufficiently large, and the power for rotating the power recovery system 108 is small. Therefore, the rotational speed of the power recovery system 108 is also low.
- the rotational speed of the power recovery system 108 is low, the rotational speed of the expander 103 is also low. This state corresponds to the “squeezed state” as referred to by the expansion valve. Therefore, the discharge temperature and discharge pressure of the first compressor 101 also gradually increase.
- the power for rotating the expander 103 and the second compressor 105 also increases, and the rotational speed of the power recovery system 108 increases.
- the rotational speed becomes high, the power recovery system 108 rotates stably due to the influence of inertial force. It is desirable to keep the first bypass path 112 open until such a stable rotation state.
- the intake temperature of the expander 103 gradually increases from substantially the same temperature as the outside air temperature at the time of stop.
- the discharge temperature (or discharge pressure) of the expander 103 is determined by the suction temperature (or suction pressure) of the expander 103.
- the suction temperature of the expander 103 and the discharge temperature of the expander 103 gradually increase as described above.
- the difference between the suction temperature and the discharge temperature also gradually increases.
- the pressure Therefore, by setting appropriate values (for example, values slightly larger than the temperature difference and the pressure difference at the time of start-up) as the predetermined values T 1 and P 1 , the start-up of the second compressor 105 (the power recovery system 108 Can be detected.
- the second compressor 105 it is possible to detect the start of the second compressor 105 based on the discharge temperature of the expander 103 or the discharge pressure of the expander 103 instead of the temperature difference ⁇ and the pressure difference ⁇ T.
- the expander 103 also rotates.
- the expander 103 sucks the working fluid and then expands and discharges the sucked working fluid. Therefore, the temperature and pressure of the working fluid discharged from the expander 103 are lower than before the suction.
- monitoring the temperature (or pressure) at the discharge port of the expander 103 in time series it can be determined that the second compressor 105 has been activated by capturing a sudden change in temperature (or pressure).
- the controller 117 sets a predetermined time t obtained experimentally or theoretically.
- the controller 117 transmits a control signal to the motor 101b of the first compressor 101 and starts measuring time with a timer.
- the controller 117 detects that “the second compressor 105 has started”.
- Predetermined time t is described in the activation control program to be executed by the controller 117.
- the time from the start of the first compressor 101 to the start of the second compressor 105 is actually measured under various operating conditions (outside air temperature or the like).
- the time which can be judged that the 2nd compressor 105 started in all the operating conditions can be set as "predetermined time t”.
- a model of the refrigeration cycle apparatus 100 is constructed, and a pressure difference necessary and sufficient to start the power recovery system 108 is estimated by computer simulation. Then, using parameters such as the volume of the first compressor 101 and the amount of working fluid in the working fluid circuit 106, the initial operation time required to create the estimated pressure difference is calculated.
- the calculated initial movement time can be set as “predetermined time t”.
- FIG. 2 is a flowchart of the start-up control of the refrigeration cycle apparatus 100.
- the refrigeration cycle apparatus 100 starts steady operation after executing the startup control shown in FIG.
- the first compressor 101 is stopped, the first bypass valve 113 is closed, the start assist valve 114 is opened, and the pressure of the working fluid in the working fluid circuit 106 is substantially uniform.
- the fan or pump for flowing the fluid (air or water) to be exchanged with the working fluid through the radiator 102 is operated after the start control is completed.
- the fan or pump for flowing the fluid to be exchanged with the working fluid to the evaporator 104 is also operated after the start control is completed.
- the controller 117 In response to obtaining the activation command from the input device 118 in step S11, the controller 117 sends a control signal to the valve opening / closing means 115 and 116 so as to open the first bypass valve 113 and close the activation auxiliary valve 114. Transmit (step S12). Accordingly, the first bypass passage 112 is opened, and the flow passage 106d is closed between the outlet of the evaporator 104 and the downstream end K2 of the first bypass passage 112.
- the controller 117 starts power supply to the motor 101b to start the first compressor 101 (step S13). Accordingly, the working fluid in the flow path 106e and the second bypass path 110 is sucked into the first compressor 101.
- the first bypass valve 113 may be opened according to the start of the first compressor 101.
- the start assist valve 114 may be closed in response to the start of the first compressor 101. In other words, there is no problem as long as the working fluid can flow through the first bypass passage 112 after the first compressor 101 is started and before the power recovery shaft 107 is rotated.
- the pressure in the flow path (flow path 106a, radiator 102, flow path 106b) from the discharge port of the first compressor 101 to the suction port of the expander 103 increases.
- the compressed working fluid also flows into the flow path 106 d between the auxiliary starting valve 114 and the suction port of the second compressor 105 through the first bypass passage 112.
- the pressure in the flow path (a part of the flow path 106d) from the auxiliary start valve 114 to the suction port of the second compressor 105 increases.
- the pressure at each suction port of the expander 103 and the second compressor 105 becomes relatively high, and the pressure at each discharge port of the expander 103 and the second compressor 105 is increased. Relatively low. That is, a pressure difference can be generated not only between the suction port and the discharge port of the expander 103 but also between the suction port and the discharge port of the second compressor 105. Since the pressure difference of the working fluid acts on each of the expander 103 and the second compressor 105, the power recovery system 108 can be easily activated independently.
- the controller 117 detects that the second compressor 105 is activated through the activation detector 119 (step S14), the valve opening / closing means 115 is closed so as to close the first bypass valve 113 and open the activation auxiliary valve 114. And 116 are transmitted to the control signal (step S15). Specifically, the controller 117 receives the detection signal from the activation detector 119, detects the activation of the second compressor 105, and then closes the first bypass valve 113 and opens the activation auxiliary valve 114. As a result, the first bypass path 112 is closed and the flow path 106d is opened. After the start control ends, the refrigeration cycle apparatus 100 shifts to a steady operation in which the working fluid is circulated through the working fluid circuit 106.
- the second bypass valve 111 that is a check valve is closed. Since the pressure in the second bypass passage 110 on the downstream side of the flow path 106e and the second bypass valve 111 is higher than the pressure in the flow path 106c, the evaporator 104, and the flow path 106d, the second bypass valve 111. Will remain closed. Thereby, the working fluid circulates through the working fluid circuit 106 during steady operation.
- the fluid pressure motor type compressor described above can be suitably used as the second compressor 105. This is because the fluid pressure motor type compressor does not substantially change the volume of the working fluid in the working chamber, so that the suction of the liquid phase working fluid can be allowed to some extent.
- a part of the second bypass passage 110 (portion from the second bypass valve 111 to the downstream end H2) can function as a buffer space for expanding the volume of the flow path 106e. Therefore, relaxation of the pulsation width of the pressure pulsation generated in the flow path 106e can be expected, and as a result, the operation reliability of the refrigeration cycle apparatus 100 can be improved.
- a part of the first bypass passage 112 (a portion from the first bypass valve 113 to the downstream end K2) can function as a buffer space for expanding the volume of the flow path 106d. Therefore, relaxation of the pulsation width of the pressure pulsation generated in the flow path 106d can be expected, and as a result, the operation reliability of the refrigeration cycle apparatus 100 can be improved.
- the rotational speed of the first compressor 101 is gradually decreased. After the first compressor 101 is stopped, the working fluid moves through the first compressor 101, the expander 103, and the second compressor 105 over a sufficient time. Therefore, the pressure difference in the working fluid circuit 106 is naturally eliminated, and becomes a substantially uniform pressure and stabilized. Thereby, the expander 103 and the 2nd compressor 105 also stop naturally.
- the pressure in the second bypass passage 110 on the downstream side of the flow passage 106e and the second bypass valve 111 decreases.
- the 2nd bypass valve 111 which is a check valve is opened.
- the working fluid in the flow path from the discharge port of the expander 103 to the auxiliary start valve 114 flows into the second bypass path 110, and together with the working fluid in the second bypass path 110 and the flow path 106e, the first compressor 101 is inhaled.
- the refrigeration cycle apparatus 100 there is a pressure difference not only between the suction port and the discharge port of the expander 103 but also between the suction port and the discharge port of the second compressor 105. Can occur. Therefore, the power recovery system 108 can be started stably and reliably, and as a result, the reliability of the refrigeration cycle apparatus 100 is improved.
- FIG. 3 is a configuration diagram of the refrigeration cycle apparatus 200 according to Embodiment 2 of the present invention.
- the refrigeration cycle apparatus 200 is different from the first embodiment in that a three-way valve is used as the first bypass valve 201. That is, the first bypass valve 201 serves as both the first bypass valve 113 and the activation assist valve 114 in the first embodiment.
- symbol is attached
- the first bypass valve 201 is provided at the junction between the downstream end K2 of the first bypass path 112 and the flow path 106d.
- the opening and closing of the first bypass path 112 and the opening and closing of the flow path 106d can be easily performed with one valve.
- the flow path 106d is opened and the first bypass path 112 is closed (for example, during steady operation)
- the first bypass path 112 is opened and the flow path 106d is
- the path of the working fluid can be easily switched between the closed state (for example, during start-up control) at the junction with the downstream end K2 of the one bypass path 112.
- the configuration of the refrigeration cycle apparatus 200 can be simplified.
- the first bypass valve 201 may be provided at the joint between the upstream end K1 of the first bypass passage 112 and the flow path 106b.
- the first bypass valve 201 is provided with a valve switching means 202.
- the valve switching means 202 is typically composed of an actuator such as a solenoid and is controlled by the controller 117.
- FIG. 4 is a flowchart of activation control of the refrigeration cycle apparatus 200.
- the refrigeration cycle apparatus 200 starts steady operation after executing the start-up control shown in FIG.
- the first compressor 101 is stopped, the flow path 106d is opened by the first bypass valve 201, and the first bypass path 112 is closed (state (a) above).
- the pressure of the working fluid in the working fluid circuit 106 is substantially uniform.
- the controller 117 In response to the acquisition of the activation command from the input device 118 in step S21, the controller 117 sends a control signal to the valve control means 202 so as to switch from the state (a) described above to the state (b). Is transmitted (step S22).
- step S23 the controller 117 starts power supply to the motor 101b to start the first compressor 101 (step S23). Accordingly, the working fluid in the flow path 106e and the second bypass path 110 is sucked into the first compressor 101.
- the process of step S22 may be executed in response to the activation of the first compressor 101.
- the pressure in the flow path 106e and the second bypass path 110 decreases.
- the second bypass valve 111 is opened, and the working fluid upstream of the second bypass valve 111, that is, the flow from the discharge port of the expander 103 to the first bypass valve 201 flows into the second bypass passage 110.
- the working fluid in the channel (the channel 106c, the evaporator 104, and part of the channel 106d) flows in.
- the working fluid that has flowed into the second bypass passage 110 is sucked and compressed by the first compressor 101 and discharged to the flow path 106a. Accordingly, the pressure in the flow path from the discharge port of the expander 103 to the first bypass valve 201 (the flow path 106c, the evaporator 104, and a part of the flow path 106d) also decreases.
- the pressure in the flow path (flow path 106a, radiator 102, flow path 106b) from the discharge port of the first compressor 101 to the suction port of the expander 103 increases.
- the compressed working fluid also flows into the flow path 106 d between the first bypass valve 201 and the suction port of the second compressor 105 through the first bypass passage 112.
- the pressure in the flow path (a part of the flow path 106d) from the first bypass valve 201 to the suction port of the second compressor 105 increases.
- the state shown in FIG. 6A is formed, and the power recovery system 108 can be easily activated independently.
- step S24 When the controller 117 detects that the second compressor 105 is started through the start detector 119 (step S24), the controller 117 switches the state from the state (b) described above to the state (a). A control signal is transmitted to the switching means 202 (step S25). Thereby, the first bypass valve 201 is switched and the first bypass passage 112 is closed. After the start control ends, the refrigeration cycle apparatus 200 shifts to a steady operation.
- a part of the second bypass passage 110 (a portion from the second bypass valve 111 to the downstream end H2) can function as a buffer space for expanding the volume of the flow path 106e. Therefore, as described in the first embodiment, it is possible to expect relaxation of the pulsation width of the pressure pulsation generated in the flow path 106e, and as a result, the reliability of the operation of the refrigeration cycle apparatus 200 can be improved.
- the first bypass path 112 can function as a buffer space for expanding the volume of the flow path 106b. Therefore, relaxation of the pulsation width of the pressure pulsation generated in the flow path 106b can be expected, and as a result, the operation reliability of the refrigeration cycle apparatus 200 can be improved.
- the pressure in the second bypass passage 110 on the downstream side of the flow passage 106e and the second bypass valve 111 decreases.
- the 2nd bypass valve 111 which is a check valve is opened.
- the working fluid in the flow path from the discharge port of the expander 103 to the first bypass valve 201 flows into the second bypass path 110, and the first compression is performed together with the working fluid in the second bypass path 110 and the flow path 106e. Inhaled into machine 101.
- the pressure loss of the working fluid to be sucked by the first compressor 101 is suppressed by avoiding the pressure loss of the working fluid by the evaporator 104 and the second compressor 105 at the time of startup. Therefore, it is possible to reduce the power with which the first compressor 101 boosts the working fluid.
- the refrigeration cycle apparatus 200 there is a pressure difference not only between the suction port and the discharge port of the expander 103 but also between the suction port and the discharge port of the second compressor 105. Can occur. Therefore, the power recovery system 108 can be started stably and reliably, and the reliability of the refrigeration cycle apparatus 200 is also improved.
- the second bypass passage 110 and the second bypass valve 111 are provided. However, these are not always necessary. That is, as shown in FIG. 5, a refrigeration cycle apparatus 300 having a configuration in which the second bypass passage 110 and the second bypass valve 111 are omitted can be proposed.
- the first bypass valve 113 is opened and the activation auxiliary valve 114 is closed at the time of activation.
- the first compressor 101 can suck only the working fluid in the flow path 106e. That is, if attention is paid to the amount of working fluid that can be sucked by the first compressor 101, the third embodiment may be more disadvantageous than the first and second embodiments.
- a pressure difference can be generated not only between the suction port and the discharge port of the expander 103 but also between the suction port and the discharge port of the second compressor 105 (FIG. 6A). reference). Therefore, even if the second bypass passage 110 and the second bypass valve 111 are omitted, the power recovery system 108 can be easily and reliably activated.
- auxiliary start valve 114 it is possible to omit the auxiliary start valve 114 from the refrigeration cycle apparatus 300.
- a pressure difference is generated only between the suction port and the discharge port of the second compressor 105.
- the drive resistance of the second compressor 105 is relatively larger than the drive resistance of the expander 103. Therefore, the state shown in FIG. 6B is more advantageous for starting the power recovery system 108 than the state shown in FIG.
- the refrigeration cycle apparatus 400 shown in FIG. 7 differs from the conventional refrigeration cycle apparatus 500 (see FIG. 9) in the position of the upstream end H1 of the bypass passage 110. Specifically, the upstream end H ⁇ b> 1 of the bypass passage 110 is located on the flow path 106 c that connects the discharge port of the expander 103 and the inlet of the evaporator 104.
- Other configurations of the refrigeration cycle apparatus 400 are the same as those of the refrigeration cycle apparatus 100 described with reference to FIG.
- a pressure difference cannot be generated between the suction port and the discharge port of the second compressor 105.
- the following significant effects can be obtained based on the difference in the position of the upstream end H1 of the bypass passage 110. That is, according to the refrigeration cycle apparatus 400, pressure loss of the working fluid due to the evaporator 104 and the second compressor 105 can be avoided in a certain period before and after the start, and thereby the working fluid that the first compressor 101 should suck The pressure drop can be suppressed. As a result, the power required for the first compressor 101 to increase the pressure of the working fluid can be reduced, and as a result, it becomes easier to form a stable operating state more quickly.
- the liquid-phase working fluid tends to accumulate in a relatively downstream portion in the evaporator 4.
- the refrigeration cycle apparatus 500 is started in a state where the liquid-phase working fluid is accumulated in the evaporator 4, the gas-phase working fluid in the flow paths 10c and 10d and the gas-phase working fluid in the evaporator 4 are separated. Then, the process proceeds through the evaporator 4 to the first compressor 1 or the second compressor 5. Since the working fluid travels a relatively long distance, the pressure loss is also relatively large. Further, there is a possibility that the liquid working fluid is sucked into the first compressor 101, and there is a possibility that the pressure loss increases due to the resistance of the liquid working fluid.
- the gas-phase working fluid flows back through the evaporator 104 and passes through the bypass 110 to the first compressor 101. Inhaled directly.
- the liquid-phase working fluid moves while vaporizing in the evaporator 104, and is sucked into the first compressor 101 through the bypass 110.
- the pressure in the evaporator 104 that is, the suction pressure of the first compressor 101 is kept substantially constant.
- the liquid-phase working fluid does not become resistive, and the pressure loss of the gas-phase working fluid is relatively small.
- the liquid phase working fluid is unlikely to be sucked into the first compressor 101 at the time of activation, more stable activation can be realized.
- the refrigeration cycle apparatus of the present invention is useful for equipment such as a water heater, an air conditioner, and a dryer.
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Abstract
Description
(1秒間あたりに第2圧縮機5が吸入できる作動流体の質量)
=108.0×Vc×N (Formula 1)
(Mass of working fluid that can be sucked by
= 108.0 × Vc × N
(1秒間あたりに膨張機3が吸入できる作動流体の質量)
=628.61×Ve×N (Formula 2)
(Mass of working fluid that the
= 628.61 × Ve × N
Vc=(628.61/108.0)×Ve≒5.8×Ve (Formula 3)
Vc = (628.61 / 108.0) × Ve≈5.8 × Ve
作動流体を圧縮する第1圧縮機、前記第1圧縮機で圧縮された作動流体を放熱させる放熱器、前記放熱器で放熱した作動流体を膨張させて作動流体から動力を回収する膨張機、前記膨張機で膨張した作動流体を蒸発させる蒸発器、前記蒸発器で蒸発した作動流体を昇圧して前記第1圧縮機に供給する第2圧縮機、およびこれらの要素をこの順番で接続している流路、によって形成された作動流体回路と、
前記膨張機で回収された動力によって前記第2圧縮機が駆動されるように、前記膨張機と前記第2圧縮機とを連結している動力回収軸と、
前記第1圧縮機の吐出口から前記膨張機の吸入口までの前記作動流体回路の部分と、前記蒸発器の出口から前記第2圧縮機の吸入口までの前記作動流体回路の部分と、を連絡する第1バイパス路と、
前記第1バイパス路に設けられ、前記第1バイパス路における作動流体の流通を制御する第1バイパス弁と、
を備えた、冷凍サイクル装置を提供する。 That is, the present invention
A first compressor that compresses the working fluid; a radiator that dissipates heat from the working fluid compressed by the first compressor; an expander that recovers power from the working fluid by expanding the working fluid dissipated by the radiator; An evaporator that evaporates the working fluid expanded by the expander, a second compressor that pressurizes the working fluid evaporated by the evaporator and supplies the working fluid to the first compressor, and these elements are connected in this order. A working fluid circuit formed by a flow path;
A power recovery shaft connecting the expander and the second compressor so that the second compressor is driven by the power recovered by the expander;
A portion of the working fluid circuit from the outlet of the first compressor to the inlet of the expander; and a portion of the working fluid circuit from the outlet of the evaporator to the inlet of the second compressor. A first bypass to communicate with,
A first bypass valve that is provided in the first bypass passage and controls the flow of the working fluid in the first bypass passage;
A refrigeration cycle apparatus is provided.
<冷凍サイクル装置100の構成>
図1は、本発明の実施の形態1における冷凍サイクル装置100の構成図である。図1に示すように、冷凍サイクル装置100は、第1圧縮機101と、放熱器102と、膨張機103と、蒸発器104と、第2圧縮機105とを、流路(配管)106a~106eにより順次接続することによって形成された作動流体回路106を備えている。作動流体として、例えば、二酸化炭素等の冷媒を用いることができる。 (Embodiment 1)
<Configuration of
FIG. 1 is a configuration diagram of a
吸入温度:10℃、吸入圧力:5.0MPa、
吐出温度:-3.0℃、吐出圧力:3.2MPa
吸入温度と吐出温度との差:13℃
吸入圧力と吐出圧力との差:1.8MPa
<定常時>
吸入温度:40℃、吸入圧力:10.0MPa
吐出温度:13.4℃、吐出圧力:4.9MPa
吸入温度と吐出温度との差:26.6℃
吸入圧力と吐出圧力との差:5.1MPa <At startup>
Suction temperature: 10 ° C., Suction pressure: 5.0 MPa,
Discharge temperature: -3.0 ° C, discharge pressure: 3.2 MPa
Difference between suction temperature and discharge temperature: 13 ° C
Difference between suction pressure and discharge pressure: 1.8 MPa
<Normal time>
Suction temperature: 40 ° C., Suction pressure: 10.0 MPa
Discharge temperature: 13.4 ° C., discharge pressure: 4.9 MPa
Difference between suction temperature and discharge temperature: 26.6 ° C
Difference between suction pressure and discharge pressure: 5.1 MPa
図2は、冷凍サイクル装置100の起動制御のフロー図である。冷凍サイクル装置100は、図2に示す起動制御の実行後、定常運転を開始する。運転待機状態において、第1圧縮機101は停止し、第1バイパス弁113は閉鎖、起動補助弁114は開放されており、作動流体回路106内の作動流体の圧力は略均一である。なお、作動流体と熱交換するべき流体(空気または水)を放熱器102に流すためのファンまたはポンプは、起動制御の終了後に作動させる。同様に、作動流体と熱交換するべき流体を蒸発器104に流すためのファンまたはポンプも起動制御の終了後に作動させる。 <Operation of the
FIG. 2 is a flowchart of the start-up control of the
本実施の形態1によれば、冷凍サイクル装置100の起動時において、第1バイパス弁113は開放、起動補助弁114は閉鎖されている。そのため、第1圧縮機101の吐出口から膨張機103の吸入口までの流路内の作動流体を、第1バイパス路112を通じて、第2圧縮機105の吸入口へ供給できる。これにより、第2圧縮機105の吸入口での圧力を上昇させることができる。また、流路106eに加えて、膨張機103の吐出口から起動補助弁114までの流路内の作動流体を、第2バイパス路110を通じて、直接、第1圧縮機101へ供給できる。 <Effect of
According to the first embodiment, when the
<冷凍サイクル装置200の構成>
図3は、本発明の実施の形態2における冷凍サイクル装置200の構成図である。図3に示すように、冷凍サイクル装置200は、第1バイパス弁201として三方弁を用いている点で、実施の形態1と相違する。つまり、第1バイパス弁201は、実施の形態1における第1バイパス弁113および起動補助弁114の両方の役割を担う。本実施の形態2において、実施の形態1と共通部品については同一符号を付し、その詳細な説明は省略する。 (Embodiment 2)
<Configuration of
FIG. 3 is a configuration diagram of the
図4は、冷凍サイクル装置200の起動制御のフロー図である。冷凍サイクル装置200は、図4に示す起動制御の実行後、定常運転を開始する。運転待機状態において、第1圧縮機101は停止し、第1バイパス弁201により流路106dは開通し、第1バイパス路112は閉鎖されている(上記(a)の状態)。作動流体回路106内の作動流体の圧力は略均一である。 <Operation of
FIG. 4 is a flowchart of activation control of the
本実施の形態2によれば、冷凍サイクル装置200の起動時において、第1バイパス路112は開通、流路106dは第1バイパス路112の下流端K2との接合部で閉鎖されている。そのため、第1圧縮機101の吐出口から膨張機103の吸入口までの流路内の作動流体を、第1バイパス路112を通じて、第2圧縮機105の吸入口へ供給できる。これにより、第2圧縮機105の吸入口での圧力を上昇させることができる。また、流路106eに加えて、膨張機103の吐出口から第1バイパス弁201までの流路内の作動流体を、第2バイパス路110を通じて、直接、第1圧縮機101へ供給できる。 <Effect of
According to the second embodiment, when the
実施の形態1および2によると、第2バイパス路110および第2バイパス弁111が設けられている。しかし、これらが常に必要というわけではない。すなわち、図5に示すように、第2バイパス路110および第2バイパス弁111を省略した構成の冷凍サイクル装置300を提案できる。 (Embodiment 3)
According to the first and second embodiments, the
図7に示す冷凍サイクル装置400は、バイパス路110の上流端H1の位置が従来の冷凍サイクル装置500(図9参照)と異なる。具体的には、バイパス路110の上流端H1が、膨張機103の吐出口と蒸発器104の入口とを結ぶ流路106c上に位置している。冷凍サイクル装置400のその他の構成は、起動の検出方法等も含め、図1等を参照して説明した冷凍サイクル装置100と同じである。 (Reference example)
The
Claims (19)
- 作動流体を圧縮する第1圧縮機、前記第1圧縮機で圧縮された作動流体を放熱させる放熱器、前記放熱器で放熱した作動流体を膨張させて作動流体から動力を回収する膨張機、前記膨張機で膨張した作動流体を蒸発させる蒸発器、前記蒸発器で蒸発した作動流体を昇圧して前記第1圧縮機に供給する第2圧縮機、およびこれらの要素をこの順番で接続している流路、によって形成された作動流体回路と、
前記膨張機で回収された動力によって前記第2圧縮機が駆動されるように、前記膨張機と前記第2圧縮機とを連結している動力回収軸と、
前記第1圧縮機の吐出口から前記膨張機の吸入口までの前記作動流体回路の部分と、前記蒸発器の出口から前記第2圧縮機の吸入口までの前記作動流体回路の部分と、を連絡する第1バイパス路と、
前記第1バイパス路に設けられ、前記第1バイパス路における作動流体の流通を制御する第1バイパス弁と、
を備えた、冷凍サイクル装置。 A first compressor that compresses the working fluid; a radiator that dissipates heat from the working fluid compressed by the first compressor; an expander that recovers power from the working fluid by expanding the working fluid dissipated by the radiator; An evaporator that evaporates the working fluid expanded by the expander, a second compressor that pressurizes the working fluid evaporated by the evaporator and supplies the working fluid to the first compressor, and these elements are connected in this order. A working fluid circuit formed by a flow path;
A power recovery shaft connecting the expander and the second compressor so that the second compressor is driven by the power recovered by the expander;
A portion of the working fluid circuit from the outlet of the first compressor to the inlet of the expander; and a portion of the working fluid circuit from the outlet of the evaporator to the inlet of the second compressor. A first bypass to communicate with,
A first bypass valve that is provided in the first bypass passage and controls the flow of the working fluid in the first bypass passage;
A refrigeration cycle apparatus comprising: - 前記蒸発器の出口から前記第2圧縮機の吸入口までの間であって前記第1バイパス路の下流端よりも前記蒸発器の近くにおいて前記作動流体回路に設けられた起動補助弁をさらに備えた、請求項1に記載の冷凍サイクル装置。 And a starting auxiliary valve provided in the working fluid circuit between the outlet of the evaporator and the inlet of the second compressor and closer to the evaporator than the downstream end of the first bypass passage. The refrigeration cycle apparatus according to claim 1.
- 前記第1バイパス弁は、前記第1バイパス路の上流端部または下流端部に設けられている、請求項2に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to claim 2, wherein the first bypass valve is provided at an upstream end portion or a downstream end portion of the first bypass passage.
- 前記第1バイパス弁は、開閉弁または三方弁である、請求項2または3に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to claim 2 or 3, wherein the first bypass valve is an on-off valve or a three-way valve.
- 前記膨張機の吐出口から前記第1バイパス路の下流端までの前記作動流体回路の部分と、前記第2圧縮機の吐出口から前記第1圧縮機の吸入口までの前記作動流体回路の部分と、を連絡する第2バイパス路をさらに備えた、請求項1~4のいずれか1項に記載の冷凍サイクル装置。 The portion of the working fluid circuit from the discharge port of the expander to the downstream end of the first bypass passage, and the portion of the working fluid circuit from the discharge port of the second compressor to the suction port of the first compressor The refrigeration cycle apparatus according to any one of claims 1 to 4, further comprising a second bypass passage that communicates with each other.
- 前記第2バイパス路に設けられ、前記第2バイパス路における作動流体の流通を制御する第2バイパス弁をさらに備えた、請求項5に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to claim 5, further comprising a second bypass valve that is provided in the second bypass passage and controls the flow of the working fluid in the second bypass passage.
- 前記第1圧縮機の起動前に、または前記第1圧縮機の起動に応じて、前記第1バイパス弁を開放する、請求項2~4のいずれか1項に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to any one of claims 2 to 4, wherein the first bypass valve is opened before starting the first compressor or in response to starting the first compressor.
- 前記第2圧縮機の起動後に、前記第1バイパス弁を閉鎖する、請求項2~4のいずれか1項に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to any one of claims 2 to 4, wherein the first bypass valve is closed after the second compressor is started.
- 前記第2圧縮機の起動を検出する起動検出器と、
前記第1バイパス弁の開閉を制御する制御器と、をさらに備え、
前記制御器は、前記起動検出器からの検出信号を受けて前記第2圧縮機の起動を検出し、前記第1バイパス弁を閉鎖する、請求項8に記載の冷凍サイクル装置。 An activation detector for detecting activation of the second compressor;
A controller for controlling opening and closing of the first bypass valve,
The refrigeration cycle apparatus according to claim 8, wherein the controller receives a detection signal from the activation detector, detects activation of the second compressor, and closes the first bypass valve. - 前記起動検出器は、前記膨張機に吸入されるべき作動流体との温度と、前記膨張機から吐出された作動流体の温度との差を検出する温度検出器であり、
前記温度差が所定の値より大きくなることで、前記第2圧縮機の起動を検出する、請求項9に記載の冷凍サイクル装置。 The activation detector is a temperature detector that detects a difference between a temperature of the working fluid to be sucked into the expander and a temperature of the working fluid discharged from the expander;
The refrigeration cycle apparatus according to claim 9, wherein the start of the second compressor is detected when the temperature difference becomes larger than a predetermined value. - 前記起動検出器は、前記膨張機に吸入されるべき作動流体の圧力と、前記膨張機から吐出された作動流体の圧力との差を検出する圧力検出器であり、
前記圧力差が所定の値より大きくなることで、前記第2圧縮機の起動を検出する、請求項9に記載の冷凍サイクル装置。 The activation detector is a pressure detector for detecting a difference between a pressure of the working fluid to be sucked into the expander and a pressure of the working fluid discharged from the expander;
The refrigeration cycle apparatus according to claim 9, wherein activation of the second compressor is detected when the pressure difference is greater than a predetermined value. - 前記起動検出器は、前記第1圧縮機の起動時点からの経過時間を計測するタイマであり、
前記タイマによって計測された時間が所定時間を経過することで、前記副第2圧縮機の起動を検出する、請求項9に記載の冷凍サイクル装置。 The activation detector is a timer that measures an elapsed time from the activation time of the first compressor,
The refrigeration cycle apparatus according to claim 9, wherein the start of the sub second compressor is detected when a predetermined time has elapsed by the time measured by the timer. - 前記第1圧縮機の起動前に、または前記第1圧縮機の起動に応じて、前記起動補助弁を閉鎖する、請求項2に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to claim 2, wherein the start assist valve is closed before the first compressor is started or in response to the start of the first compressor.
- 前記第2圧縮機の起動後に、前記起動補助弁を開放する、請求項2に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to claim 2, wherein the start auxiliary valve is opened after the second compressor is started.
- 前記第2圧縮機の起動を検出する起動検出器と、
前記起動補助弁の開閉を制御する制御器と、をさらに備え、
前記制御器は、前記起動検出器からの検出信号を受けて前記第2圧縮機の起動を検出し、前記起動補助弁を開放する、請求項14に記載の冷凍サイクル装置。 An activation detector for detecting activation of the second compressor;
A controller for controlling opening and closing of the start assist valve,
The refrigeration cycle apparatus according to claim 14, wherein the controller receives a detection signal from the activation detector, detects activation of the second compressor, and opens the activation assist valve. - 前記起動検出器は、前記膨張機に吸入されるべき作動流体との温度と、前記膨張機から吐出された作動流体の温度との差を検出する温度検出器であり、
前記温度差が所定の値より大きくなることで、前記第2圧縮機の起動を検出する、請求項15に記載の冷凍サイクル装置。 The activation detector is a temperature detector that detects a difference between a temperature of the working fluid to be sucked into the expander and a temperature of the working fluid discharged from the expander;
The refrigeration cycle apparatus according to claim 15, wherein the start of the second compressor is detected when the temperature difference becomes larger than a predetermined value. - 前記起動検出器は、前記膨張機に吸入されるべき作動流体の圧力と、前記膨張機から吐出された作動流体の圧力との差を検出する圧力検出器であり、
前記圧力差が所定の値より大きくなることで、前記第2圧縮機の起動を検出する、請求項15に記載の冷凍サイクル装置。 The activation detector is a pressure detector for detecting a difference between a pressure of the working fluid to be sucked into the expander and a pressure of the working fluid discharged from the expander;
The refrigeration cycle apparatus according to claim 15, wherein the activation of the second compressor is detected when the pressure difference becomes larger than a predetermined value. - 前記起動検出器は、前記第1圧縮機の起動時点からの経過時間を計測するタイマであり、
前記タイマによって計測された時間が所定時間を経過することで、前記副第2圧縮機の起動を検出する、請求項15に記載の冷凍サイクル装置。 The activation detector is a timer that measures an elapsed time from the activation time of the first compressor,
The refrigeration cycle apparatus according to claim 15, wherein the start of the sub second compressor is detected when a predetermined time has elapsed by the time measured by the timer. - 前記膨張機と前記第2圧縮機とが1つの密閉容器に収容されている、請求項1~18のいずれか1項に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to any one of claims 1 to 18, wherein the expander and the second compressor are accommodated in a single sealed container.
Priority Applications (4)
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JP2010543836A JPWO2010073586A1 (en) | 2008-12-22 | 2009-12-21 | Refrigeration cycle equipment |
US13/140,331 US20110247358A1 (en) | 2008-12-22 | 2009-12-21 | Refrigeration cycle apparatus |
CN200980151528.6A CN102257332B (en) | 2008-12-22 | 2009-12-21 | Refrigeration cycle device |
EP09834397.3A EP2381190A4 (en) | 2008-12-22 | 2009-12-21 | Refrigeration cycle device |
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EP (1) | EP2381190A4 (en) |
JP (1) | JPWO2010073586A1 (en) |
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JP2020051630A (en) * | 2018-09-21 | 2020-04-02 | 株式会社富士通ゼネラル | Refrigeration cycle device |
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KR101904870B1 (en) * | 2012-01-30 | 2018-10-08 | 엘지전자 주식회사 | Apparatus and method for controlling compressor, and refrigerator having the same |
KR101955977B1 (en) * | 2012-01-30 | 2019-03-08 | 엘지전자 주식회사 | Apparatus and method for controlling compressor, and refrigerator having the same |
JP6197745B2 (en) * | 2013-07-31 | 2017-09-20 | 株式会社デンソー | Refrigeration cycle equipment for vehicles |
JP6276000B2 (en) * | 2013-11-11 | 2018-02-07 | 株式会社前川製作所 | Expander-integrated compressor, refrigerator, and operation method of refrigerator |
KR102016827B1 (en) | 2015-05-01 | 2019-08-30 | 가부시끼가이샤 마에가와 세이사꾸쇼 | How to operate freezer and freezer |
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US20110247358A1 (en) | 2011-10-13 |
EP2381190A1 (en) | 2011-10-26 |
CN102257332A (en) | 2011-11-23 |
CN102257332B (en) | 2013-08-14 |
JPWO2010073586A1 (en) | 2012-06-07 |
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