JP5605191B2 - heat pump - Google Patents

Description

The present invention also relates to a heat pump.

  As a heat supply system, a configuration is generally known in which the heat of steam generated by a boiler is transmitted to an object (see, for example, Patent Document 1). In addition, a configuration is known in which heat from a heat pump or refrigerator medium is transmitted to an object.

JP-A-6-249450

  An aspect of the present invention aims to provide a heat pump and a heat supply system with high energy efficiency.

According to the aspect of the present invention, the heat absorption part, the compression part, the heat radiation part, the expansion part, and the return of part of the fluid from the outlet of the compression part toward the heat radiation part are returned to the inlet of the compression part. An ejector fluidly connected to a path and an inlet of the compression section, wherein the fluid from the return path is input as a high pressure fluid and the fluid from the heat absorption section is input as a low pressure fluid And a control device that performs operation control in a load state between a full load including a partial load state and a no-load state, and the control device inputs the fluid that is input to the ejector according to a load factor in the partial load operation A heat pump for controlling the ratio of
Also, a heat absorption part, a compression part, a heat radiation part, an expansion part, a return path for returning a part of the fluid from the outlet of the compression part toward the heat radiation part to the inlet of the compression part, and the compression part An ejector that is fluidly connected to an inlet of the gas generator, wherein the fluid from the return path is input as a high-pressure fluid and the fluid from the heat absorption unit is input as a low-pressure fluid; And a control device that controls the operation in a load state between a full load and a no load, the control device causing the fluid to be input to the ejector during partial load operation, and the fluid to be ejected during full load operation. There is provided a heat pump that sets the path of the fluid so as not to be input to the fluid.
Also, a heat absorption part, a compression part, a heat radiation part, an expansion part, a return path for returning a part of the fluid from the outlet of the compression part toward the heat radiation part to the inlet of the compression part, and the compression part An ejector that is fluidly connected to an inlet of the gas outlet, wherein the fluid from the return path is input as a high-pressure fluid, and the fluid from the heat absorption unit is input as a low-pressure fluid, and via the ejector And a bypass path that guides the fluid from the heat absorption part to the compression part, and the ejector includes a plurality of auxiliary ejectors having different nozzle shapes, one of which is selectively used. A heat pump is provided.
Also, a heat absorption part, a compression part, a heat radiation part, an expansion part, a return path for returning a part of the fluid from the outlet of the compression part toward the heat radiation part to the inlet of the compression part, and the compression part An ejector that is fluidly connected to an inlet of the discharge port, wherein the fluid from the return path is input as a high-pressure fluid and the fluid from the heat absorption unit is input as a low-pressure fluid; and the expansion unit There is provided a heat pump comprising: a pipe that guides a part of the fluid from the outlet of the heat radiating section toward the return path.

  According to another aspect of the present invention, a heat supply system including the heat pump of the above aspect is provided to supply heat to an external device serving as a heat demand unit.

  According to the heat pump and the heat supply system, the power of the compressor is reduced and the energy efficiency is improved by applying the ejector at the inlet of the compression unit.

It is the schematic which shows one Embodiment. It is a figure which shows an example of the performance curve of the compressor in a heat pump. It is a figure which shows the relationship between the temperature of the low-temperature heat source in a heat pump, and partial load efficiency. It is a schematic diagram which shows an example of a structure of an ejector. It is a graph which shows the relationship between a load factor and the motive power of a compression part based on a trial calculation result. It is a graph which shows the relationship between a load factor and COP based on the said calculation result. It is a figure which shows deformation | transformation embodiment. It is a figure which shows another deformation | transformation embodiment. It is the schematic which shows a heat supply system.

  Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a schematic view showing a heat pump 10.

  The heat pump 10 is a circuit that transfers heat between a plurality of objects by using a change in the state of a working fluid by a cycle including evaporation, compression, condensation, and expansion processes. A heat pump cycle generally has the advantage of being relatively energy efficient.

  In the present embodiment, the heat pump 10 has a heat absorption part 12, a compression part 14, a heat radiation part 16, and an expansion part 18, which are connected via a conduit. In the heat pump 10, the working fluid flows in the conduit. Further, the heat pump 10 includes a control device 20. The control device 20 can control the heat pump 10 in an integrated manner.

  In the heat absorption part 12, the working fluid flowing through the main path 25 absorbs heat from a heat source outside the cycle (low temperature heat source). In this embodiment, the heat absorption part 12 of the heat pump 10 includes an evaporator in which the working fluid evaporates. Heat from the outside is absorbed by the heat absorption part 12 of the heat pump 10.

  The compression unit 14 compresses the working fluid by a compressor or the like. At this time, the temperature of the working fluid usually increases. The compression unit 14 may have a single-stage compression structure or a multistage compression structure that compresses the working fluid into a plurality of stages. The number of compression stages is set according to the specifications of the heat pump 10 and can be 1, 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. Among the various compressors such as an axial flow compressor, a centrifugal compressor, a reciprocating compressor, and a rotary compressor, a compressor suitable for compressing a working fluid is applied. Power is supplied to the compressor. In the compression part 14 which has a multistage compression structure, a multiaxial compression structure or a coaxial compression structure is applicable.

  The heat radiating section 16 has a conduit through which the working fluid compressed by the compressing section 14 flows, and gives heat of the working fluid flowing in the main path 25 to a heat source (heated fluid) outside the cycle. In the present embodiment, the heat dissipation unit 16 of the heat pump 10 includes a condenser in which the working fluid is condensed. The number of heat radiating portions is set according to the specifications of the heat pump 10, and can be 1, 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more.

  The expansion unit 18 expands the working fluid by a pressure reducing valve (expansion valve) or a turbine. At this time, the temperature of the working fluid usually decreases. When a turbine is used, power can be taken out from the expansion unit 18, and the power may be supplied to the compression unit 14, for example. As the working fluid used for the heat pump 10, various known heat media such as a fluorocarbon medium (HFC 245fa, R134a, etc.), ammonia, water, carbon dioxide, air, etc. are used. Used according to specifications and heat balance. At least a part of the working fluid flowing through the heat radiating unit 16 of the heat pump 10 may be in a supercritical state.

  In the present embodiment, the control device 20 can control the operation of the heat pump 10 in a load state between a full load including a partial load state and no load. FIG. 2 is a diagram illustrating an example of a performance curve of a compressor in a heat pump. In general, in a heat pump, as shown in FIGS. 2 and 3, the performance curve may change depending on the temperature of a low-temperature heat source. In general, the COP of the heat pump varies depending on the load. In general, in a heat pump, there is a case where the partial load efficiency is higher than the constant load efficiency. That is, there are cases where the overall efficiency is relatively high when the output ratio of the heat pump is lowered. Specifically, when the temperature of the low-temperature heat source is high, that is, when the pressure ratio is small, the partial load efficiency may be relatively high. In the present embodiment, the energy efficiency is improved by controlling the entire system S1 including the partial load operation of the heat pump 10.

  In the present embodiment, the heat pump 10 includes a return path 30 that returns a part of the working fluid from the outlet of the compressing unit 14 toward the heat radiating unit 16 to the inlet of the compressing unit 14. One end of the return path 30 is fluidly connected to a branch part 31 provided in a pipe 27 that connects the outlet of the compression part 14 and the inlet of the heat dissipation part 16. The other end of the return path 30 is fluidly connected to a merging portion 33 provided in a pipe 29 that fluidly connects the outlet of the heat absorbing portion 12 and the inlet of the compressing portion 14.

  At least a part of the working fluid from the compressing unit 14 can be guided to the heat radiating unit 16 via the branch unit 31. Further, a part of the working fluid from the compression unit 14 can be guided to the return path 30 via the branch portion 31. In the present embodiment, the branch section 31 includes a valve 35 that can be switched to a predetermined branch ratio (throttle). The branch ratio (the ratio of the working fluid branched from the main flow) in the valve 35 is set according to the specifications of the heat pump 10 and / or the system including the heat pump 10, the heat balance, and the like. 20, 25, 30, 35, 40, 45, 50, 55, 60, 65, 70, 75, 80, 85, 90, or 95%.

  In the merging portion 33, the working fluid from the return path 30 and the working fluid from the heat absorbing portion 12 can be mixed. In the present embodiment, the merging portion 33 has an ejector 37. The ejector 37 receives a working fluid from the outlet (branch unit 31) of the compression unit 14 via the return path 30 as a high-pressure fluid, and receives a working fluid from the outlet of the heat absorbing unit 12 as a low-pressure fluid. Is done.

  FIG. 4 is a schematic diagram illustrating an example of the configuration of the ejector 37. In FIG. 4, the ejector 37 includes a main body portion 41 and a nozzle portion 43. The nozzle portion 43 has a cylindrical shape with a smaller diameter than the main body portion 41 and is arranged inside the main body portion 41. The main body portion 41 has a cylindrical shape surrounding at least a part of the nozzle portion 43. Further, the nozzle portion 43 has an opening 45 opened in the internal space of the main body portion 41. In FIG. 4, the main body 41 has a channel cross-sectional area that varies along the axial direction (flow direction). In one example, the cross-sectional area of the flow path in the main body 41 gradually decreases from the fluid inlet, and becomes minimum in the vicinity of the arrangement position of the opening 45 of the nozzle 43 in the axial direction. Moreover, the flow path cross-sectional area in the main body 41 gradually increases from the minimum position toward the outlet.

  In the ejector 37, the working fluid from the heat absorbing part 12 flows through the flow path inside the nozzle part 43. In addition, the working fluid from the outlet (branch portion 31) of the compression unit 14 flows through a channel (a channel outside the nozzle unit 43) formed between the nozzle unit 43 and the main body unit 41. The ejector 37 is not limited to the configuration in FIG. 4, and various configurations can be applied.

  In the present embodiment, a higher pressure is obtained at the outlet of the ejector 37 than the outlet of the heat absorbing unit 12 due to the effect of the high pressure fluid. As a result, it is possible to reduce the power of the compressor 14 (compressor) and improve the coefficient of performance (COP) of the heat pump 10 at the time of partial load.

  An example of a trial calculation of the effect of the combination of the partial load operation and the ejector at the compressor inlet is shown below. Trial calculations were made for cases where the load factor in the partial load operation was (a) 25%, (b) 50%, and (c) 75%. In each of the above load factors, the throttle ratio (the ratio of the working fluid branched from the main flow) is (a) 75%, (b) 50%, and (c) 25%, respectively. The enthalpies of the compression section inlet, the heat insulation point, and the compression section outlet were 423.44 kJ / kg, 440.47 kJ / kg, and 444.73 kJ / kg, respectively. P1, p2, p3, p4: pressure, ρ1, ρ2, ρ3, ρ4: density, h1, h2, h3, h4: enthalpy, v1, v2, v3, v4: flow velocity. The following is derived from Bernoulli's theorem and the law of conservation of energy.

(A) When the load factor is 25%, with respect to the working fluid from the compressor, at the compressor outlet, p1: 3244 kPa, ρ1: 178.49 kg / m ³ , h1: 444.73 kJ / kg, v1: 0 m / s , Flow rate ratio (throttle): 75%. In the ejector, p2: 1318 kPa, ρ2: 58.24 kJ / m ³ , h2: 444.73 kJ / kg, v2: 192.85 m / s. Further, in the vicinity of the opening of the nozzle portion of the ejector, p2 is 1318 kPa, ρ2 is 58.24 kg / m ³ , h2 is 444.73 kJ / kg, and v2 is 167.01 m / s. On the other hand, for the working fluid from the endothermic part (evaporator), at the endothermic part outlet (evaporator outlet), p3: 1318 kPa, ρ3: 66.27 kg / m ³ , h3: 423.44 kJ / kg, v3: 0 m / s. . In the vicinity of the opening of the nozzle portion of the ejector, p3: 1318 kPa, ρ3: 66.27 kg / m ³ , h3: 423.44 kJ / kg, v3: 167.01 m / s. For the mixed fluid, immediately after mixing, p3: 1318 kPa, ρ3: 61.89 kg / m ³ , h3: 439.41 kJ / kg, v3: 167.01 m / s, and flow rate ratio: 100%. Further, at the outlet of the ejector whose flow path is enlarged, p4: 2602.22 kPa, ρ4: 108.29 kg / m ³ , h4: 439.41 kJ / kg, v4: 0 m / s, and flow rate ratio: 100%. The power of the compression section is 21.29 kJ / kg when the ejector is not applied, and 5.32 kJ / kg when the ejector is applied.

(B) When the load factor is 50%, for the working fluid from the compressor, p1: 3244 kPa, ρ1: 178.49 kg / m ³ , h1: 444.73 kJ / kg, v1: 0 m / s at the compressor outlet. The flow rate ratio (throttle): 50%. In the ejector, p2: 1318 kPa, ρ2: 58.24 kJ / m ³ , h2: 444.73 kJ / kg, v2: 192.85 m / s. Further, in the vicinity of the opening of the nozzle portion of the ejector, p2 is 1318 kPa, ρ2 is 58.24 kg / m ³ , h2 is 444.73 kJ / kg, and v2 is 136.36 m / s. On the other hand, for the working fluid from the endothermic part (evaporator), at the endothermic part outlet (evaporator outlet), p3: 1318 kPa, ρ3: 66.27 kg / m ³ , h3: 423.44 kJ / kg, v3: 0 m / s. . Also, in the vicinity of the opening of the nozzle portion of the ejector, p3: 1318 kPa, ρ3: 66.27 kg / m ³ , h3: 423.44 kJ / kg, v3: 136.36 m / s. For the mixed fluid, immediately after mixing, p3: 1318 kPa, ρ3: 61.89 kg / m ³ , h3: 434.09 kJ / kg, v3: 136.36 m / s, and flow rate ratio: 100%. Further, at the outlet of the ejector whose flow path is enlarged, p4: 2082 kPa, ρ4: 108.29 kg / m ³ , h4: 434.09 kJ / kg, v4: 0 m / s, and flow rate ratio: 100%. The power of the compression unit is 21.29 kJ / kg when the ejector is not applied, and 10.65 kJ / kg when the ejector is applied.

(C) When the load factor is 75%, for the working fluid from the compressor, at the compressor outlet, p1: 3244 kPa, ρ1: 178.49 kg / m ³ , h1: 444.73 kJ / kg, v1: 0 m / s , Flow rate ratio (throttle): 25%. In the ejector, p2: 1318 kPa, ρ2: 58.24 kJ / m ³ , h2: 444.73 kJ / kg, v2: 192.85 m / s. Further, in the vicinity of the opening of the nozzle portion of the ejector, p2 is 1318 kPa, ρ2 is 58.24 kg / m ³ , h2 is 444.73 kJ / kg, and v2 is 96.42 m / s. On the other hand, for the working fluid from the endothermic part (evaporator), at the endothermic part outlet (evaporator outlet), p3: 1318 kPa, ρ3: 66.27 kg / m ³ , h3: 423.44 kJ / kg, v3: 0 m / s. . In the vicinity of the opening of the nozzle portion of the ejector, p3: 1318 kPa, ρ3: 66.27 kg / m ³ , h3: 423.44 kJ / kg, v3: 96.42 m / s. For the mixed fluid, immediately after mixing, p3: 1318 kPa, ρ3: 61.89 kg / m ³ , h3: 428.76 kJ / kg, v3: 96.42 m / s, flow rate ratio: 100%. Further, at the outlet of the ejector whose flow path is enlarged, p4: 1660.49 kPa, ρ4: 80.83 kg / m ³ , h4: 428.76 kJ / kg, v4: 0 m / s, and the flow rate ratio: 100%. The power of the compression unit is 21.29 kJ / kg when the ejector is not applied, and 15.97 kJ / kg when the ejector is applied.

  FIG. 5 is a graph showing the relationship between the load factor and the power of the compression unit based on the above estimation results. FIG. 6 is a graph showing the relationship between the load factor and the COP based on the result of the trial calculation. FIG. 5 shows that the power of the compressor (compressor) during partial load is reduced by applying the ejector. FIG. 6 shows that the COP at the time of partial load is improved by applying the ejector.

  FIG. 7 is a view showing a modified embodiment of the heat pump 10 shown in FIG. In the following description, the same components as those in the above embodiment (FIG. 1) are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  In the heat pump 10 </ b> A shown in FIG. 7, the merging portion 33 includes a plurality of ejectors (auxiliary ejectors) 37 </ b> A, 37 </ b> B, 37 </ b> C, valves 38 </ b> A, 38 </ b> B, and a bypass path 39. The ejectors 37A, 37B, and 37C have different nozzle shapes. The bypass path 39 fluidly connects the heat absorption part 12 and the compression part 14 without going through the ejectors 37A, 37B, and 37C, and compresses the working fluid from the heat absorption part 12 without going through the ejectors 37A to 37C. Guide to section 14. In the bypass path 39, the working fluid from the heat absorption unit 12 bypasses the ejectors 37 </ b> A, 37 </ b> B, and 37 </ b> C and travels toward the compression unit 14. The valve 38 </ b> A or 38 </ b> B has a switching mechanism for selecting the destination of the working fluid from the return path 30 or the heat absorption unit 12 from the ejector 37 </ b> A, the ejector 37 </ b> B, the ejector 37 </ b> C, and the bypass path 39.

  In the present embodiment, the control device 20 switches and controls the valves 38A and 38B according to the system specifications, heat balance, partial load factor, etc., and the working fluid path from the return path 30 to the compression unit 14 and the heat absorption. The working fluid path from the section 12 to the compression section 14 can be set. In one example, a route passing through the ejector 37A, the ejector 37B, or the ejector 37C is selected in the case of partial load operation, and a route passing through the bypass route 39 is selected in the full load operation without passing through the ejector. The According to the partial load factor or the like, an optimum one for reducing the power of the compressor 14 can be selected from the ejectors 37A, 37B, and 37C. In the heat pump 10A, the energy efficiency can be further improved by optimizing the nozzle shape of the ejector.

  FIG. 8 is a view showing another modified embodiment of the heat pump 10 shown in FIG. In the following description, the same components as those in the above embodiment (FIG. 1) are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  The heat pump 10 </ b> B illustrated in FIG. 8 includes a branch portion 51 provided at the outlet of the heat radiating portion 16 and a pipe 53 that fluidly connects the branch portion 51 and the return path 30.

  At least a part of the working fluid from the heat radiating unit 16 can be guided to the expansion unit 18 via the branch unit 51. In addition, a part of the working fluid from the heat radiating unit 16 toward the expansion unit 18 can be guided to the return path 30 via the branch unit 51 and the pipe 53. In the present embodiment, the branch portion 51 has a valve 55 that can be switched to a predetermined branch ratio (throttle). The branching ratio (the ratio of the working fluid branched from the main flow) in the valve 55 is set according to the specifications of the heat pump 10 and / or the system including the heat pump 10 and the heat balance, for example, about 0, 5, 10, 15 20, 25, 30, 35, 40, 45, 50, 55, 60, 65, 70, 75, 80, 85, 90, or 95%.

  In the present embodiment, the control device 20 switches and controls the valve 55 according to the system specifications, heat balance, partial load factor, and the like, and compresses part of the working fluid from the heat radiating unit 16 via the return path 30. It can be returned to the entrance of section 14. By performing such flow control when the heat exchange performance of the heat radiating unit 16 is reduced, it is possible to suppress the decrease in COP.

  FIG. 9 is a schematic diagram showing a heat supply system S1 including the heat pump 10 shown in FIG.

  As shown in FIG. 9, the heat supply system S1 includes a heat pump 10 (exhaust heat recovery type heat pump) through which a working fluid (first fluid) flows, a low-temperature heat source device (exhaust heat recovery device, heat recovery device) 150, and a control. And a device 20. The control device 20 controls the entire system in an integrated manner. The configuration of the system S1 can be variously changed according to design requirements.

  In the present embodiment, heat from the heat supply system S1 is supplied to the external device 190 serving as a heat demand unit. In the present embodiment, the heat pump 10 is an exhaust heat recovery type heat pump that can use at least part of the exhaust heat from the external device 190 (exhaust heat source). In another embodiment, the heat pump 10 can be configured to be able to use at least part of the exhaust heat from other exhaust heat sources other than the external device 190. In the present embodiment, the heat pump 10 can heat the heated fluid (second fluid, air, etc.) flowing through the air supply path 115 using the heat of the working fluid.

  In the present embodiment, the heat absorption part of the heat pump 10 can absorb (recover) the heat (exhaust heat) of the exhaust fluid (exhaust gas, exhaust air) from the external device 190 via the low-temperature heat source device 150. In the present embodiment, the heat absorption part of the heat pump 10 includes an evaporator that is thermally connected to the heat radiation part (low temperature heat supply pipe 119) of the low temperature heat source device 150 and in which the working fluid evaporates. The heat of the medium flowing through the heat radiation unit of the low-temperature heat source device 150 is absorbed by the heat absorption unit of the heat pump 10. The heat absorption part of the heat pump 10 may be configured to additionally absorb the heat of other heat sources such as the atmosphere. The heat pump 10 can further include a bypass path, a flow rate sensor, a flow path control valve, and the like.

  The air supply path 115 through which the air heated by the heat pump 10 flows has a conduit through which the fluid to be heated flows, a fluid driving device such as a pump and a blower, a valve for fluid control, a gas processing device such as a filter, and the like as necessary. be able to.

  In the present embodiment, the output temperature of the fluid to be heated (drying air) from the air supply path 115 can be changed according to the heat demand. The output temperature can be, for example, 50, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190, or 200 ° C. or higher.

  In addition, the heat supply system S1 may include an auxiliary heat source (supplemental heat supply device). A boiler, electric heater, and / or other heat device can be used as an auxiliary heat source. A boiler burns fuels, such as oil and gas, and heats a heat carrier (water etc.) with the combustion heat. Various known forms can be applied as the boiler.

  In the present embodiment, the external device 190 is a heating chamber in which a fluid to be heated (second fluid) is supplied and the object is heated, for example. In the present embodiment, the fluid to be heated (second fluid) is air. In the present embodiment, high-temperature air heated by the heat pump 10 (and / or auxiliary heat source) is supplied to the external device 190. In the external device 190, heat from the high temperature air is transmitted to the object.

  In the present embodiment, in the external device (heating chamber) 190, heat from the heated air is directly or indirectly transmitted to the object. For example, in the external device 190, heated air can directly contact an object. Alternatively, in the external device 190, another substance can be interposed between the heated air and the object.

  In the present embodiment, the heating object is an industrial part or an industrial material. For example, in an external device (heating chamber) 190, at least a part of industrial parts or industrial materials is dried. Alternatively, in the external device 190, at least a part of the industrial part or the industrial material is heat-treated. Sludge, paper, wood, resin, chemicals, chemicals, sand, household waste, industrial waste, crafts, craft materials, electrical parts, electrical equipment, paints, industrial clothing, machine parts, mechanical products, food, foodstuffs Various objects such as food products can be heated. In other embodiments, the fluid to be heated can be air other than drying or a fluid other than air. Examples of the heated fluid other than air include water, compressed water, chemicals, and viscous liquids. In another embodiment, the external device (heating chamber) 90 can include a drying device and / or a heat utilization device other than the drying device.

  The external device 190 includes a fluid inlet portion, a fluid outlet portion, an exhaust route, and a transfer device (not shown) as necessary. In one example, the transfer device can have various forms such as a conveyor, a transport vehicle, and a transport robot. The object to be heated is put into the external device (heating chamber) 190 and taken out from the external device 190 by the transfer device. Alternatively or additionally, the external device 190 may include an output unit having a gate type, a swivel type, or the like for outputting an object after heating. The output part of the heated object can have a mechanism for performing a predetermined process such as a chemical process on the heated object as necessary.

  In the present embodiment, the transfer device can move the heating object in the external device (heating chamber) 190 as necessary. The external device 190 further includes a dehydrating device (not shown) as needed, thereby dehydrating the object. During the dehydration, a flocculant can be added to the object as necessary. Various forms such as a centrifugal type, a pressure type, a pressure type, and a vibration type can be applied to the dehydration depending on the object. Dehydration reduces the volume of the object. In addition, the external device 190 can further include a preheating chamber that applies heat to the object before entering the external device 190 as necessary.

  The low-temperature heat source device 150 serving as an exhaust heat recovery device includes a heat recovery unit that recovers exhaust heat from the external device 190 (and another heat device (not shown) if necessary). In addition, the low-temperature heat source device 150 can be configured to include a heat storage tank that at least temporarily stores heat recovered from the heat recovery unit, and a heat dissipation unit.

  The heat recovery unit of the low-temperature heat source device 150 is thermally connected to the exhaust heat recovery pipe (exhaust pipe) 117 through which exhaust from the external apparatus (heating chamber) 190 (and another heat apparatus) flows, and the exhaust heat recovery pipe. And an endothermic conduit through which the heat medium flows. In another embodiment, the heat recovery unit may be configured to recover exhaust heat from the external device 190 (and another heat device) without going through exhaust.

  In the present embodiment, as described above, the power of the compressor during partial load operation is reduced by applying the ejector at the compressor inlet of the heat pump 10. Therefore, according to this embodiment, the energy efficiency of the entire system S1 can be improved by the partial load operation of the heat pump 10 and the fluid control using the ejector at the compressor inlet.

  As mentioned above, although embodiment of this invention was described, this invention is not limited to these embodiment. The numerical value used in the above description is an example, and the present invention is not limited to this. Additions, omissions, substitutions, and other modifications can be made without departing from the spirit of the present invention. The present invention is not limited by the above description, but only by the appended claims.

  S1: heat supply system, 10, 10A, 10B: heat pump, 12: heat absorption part, 14: compression part, 16: heat dissipation part, 18: expansion part, 20: control device, 25: main path, 30: return path, 31 : Branching part, 33: Junction part, 35: Valve, 37: Ejector, 37A, 37B, 37C: Ejector (complementary ejector) 38: Valve, 39: Bypass path, 41: Main body part, 43: Nozzle part, 45: Opening .

Claims (4)

An endothermic part;
A compression section;
A heat dissipating part;
An inflatable part;
A return path for returning a part of the fluid from the outlet of the compression unit toward the heat dissipation unit to the inlet of the compression unit;
An ejector fluidly connected to an inlet of the compression unit, wherein the fluid from the return path is input as a high pressure fluid and the fluid from the heat absorption unit is input as a low pressure fluid;
A control device that performs operation control in a load state between a full load and a no load including a partial load state ,
The said control apparatus controls the ratio of the said fluid input into the said ejector according to the load factor in partial load driving | operation
A heat pump characterized by that. An endothermic part,
A compression section;
A heat dissipating part;
An inflatable part;
A return path for returning a part of the fluid from the outlet of the compression unit toward the heat dissipation unit to the inlet of the compression unit;
An ejector fluidly connected to an inlet of the compression unit, wherein the fluid from the return path is input as a high pressure fluid and the fluid from the heat absorption unit is input as a low pressure fluid;
A control device that performs operation control in a load state between a full load and a no load including a partial load state ,
The controller sets the fluid path so that the fluid is input to the ejector during partial load operation and the fluid is not input to the ejector during full load operation.
A heat pump characterized by that. An endothermic part;
A compression section;
A heat dissipating part;
An inflatable part;
A return path for returning a part of the fluid from the outlet of the compression unit toward the heat dissipation unit to the inlet of the compression unit;
An ejector fluidly connected to an inlet of the compression unit, wherein the fluid from the return path is input as a high pressure fluid and the fluid from the heat absorption unit is input as a low pressure fluid;
A bypass path for guiding the fluid from the heat absorption part to the compression part without passing through the ejector ,
The ejector includes a plurality of auxiliary ejectors having different nozzle shapes, one of which is selectively used . An endothermic part;
A compression section;
A heat dissipating part;
An inflatable part;
A return path for returning a part of the fluid from the outlet of the compression unit toward the heat dissipation unit to the inlet of the compression unit;
An ejector fluidly connected to an inlet of the compression unit, wherein the fluid from the return path is input as a high pressure fluid and the fluid from the heat absorption unit is input as a low pressure fluid;
A pipe for guiding a part of the fluid from the outlet of the heat dissipating part toward the expanding part to the return path ,
A heat pump characterized by that.

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