JP6195235B2 - Steam injector and heat pump device - Google Patents

Description

  The present invention relates to a steam injector and a heat pump apparatus using the same.

  Conventionally, a refrigeration cycle using an ejector has been disclosed (see, for example, Patent Document 1 and Non-Patent Document 1). In this refrigeration cycle, the energy that was lost as a vortex in the expansion valve in the refrigeration cycle is recovered as work of the compressor by the ejector, thereby realizing a high-efficiency refrigeration cycle with improved COP. It is said that there is.

  On the other hand, a small steam injector having a throat portion with an inner diameter of 6.0 mm is disclosed (for example, see Non-Patent Document 2). According to this steam injector, a higher discharge pressure is obtained compared to the input steam pressure.

Japanese Patent No. 3219108

Takeuchi et al., "Development of the world's first ejector cycle refrigerator", Denso Technical Review, vol. 14 (December 2009), 65-75 Y. Abe et al., “Model development of turbulent dispersion force for advanced two-fluid model in consideration of bubble-liquid phase interactions”, Proceedings of the 18th International Conference on Nuclear Engineering (ICONE-18) ICONE18-29517, 2010. Narabayashi et al., "Study on High Performance Steam Injector (1st Report, Formulation and Characteristic Analysis of Operating Mechanism)", Transactions of the Japan Society of Mechanical Engineers, Volume B, Vol. 62, No. 597, 1996 (1996) ) May, page 1833

  However, as disclosed in Non-Patent Document 2, there is a problem that when the steam injector is downsized, the amount of refrigerant discharged is reduced accordingly.

  The present invention has been made in view of the above, and an object of the present invention is to provide a steam injector that is small but has a large discharge amount, and a heat pump device using the same.

  In order to solve the above-described problems and achieve the object, a steam injector according to the present invention includes an introduction portion that introduces a liquid flow of the refrigerant and the vapor flow of the refrigerant, and an internal portion toward the traveling direction of the liquid flow. A mixing portion that has a shape with a reduced cross-sectional area, and mixes the liquid flow and the vapor flow in the form of a jet to form a refrigerant flow; and a throat portion formed on the output side of the mixing portion; A plurality of unit steam injectors, each having a shape in which an internal cross-sectional area expands from the throat portion toward the traveling direction of the refrigerant flow, and a diffuser portion that discharges the pressured refrigerant flow from the discharge portion And a liquid flow path and a vapor flow path for supplying each of the liquid flow and the vapor flow of the refrigerant to each introduction portion of each unit vapor injector.

  The steam injector according to the present invention is the steam injector according to the above invention, wherein the steam injector is formed by joining a set of constituent members, and each of the set of constituent members includes the introduction portion, the mixing portion, A groove or a hole having a shape obtained by dividing the throat part and the diffuser part into a plurality of parts is formed, and the introduction part, the mixing part, the throat part, and the diffuser part are joined to the set of constituent members. The groove is formed by the groove or the hole.

  In the steam injector according to the present invention, in the above invention, the set of constituent members is plate-shaped and joined to each other in a stacked state, and at least two of the plurality of unit steam injectors are It arrange | positions along the main surface of a plate-shaped structural member, It is characterized by the above-mentioned.

  The steam injector according to the present invention is characterized in that, in the above-mentioned invention, a flow path is formed which communicates the introduction portions of the unit steam injectors arranged along the main surface of the plate-like component.

  In the steam injector according to the present invention, in the above invention, the set of constituent members is plate-shaped and joined to each other in a stacked state, and at least two of the plurality of unit steam injectors are It arrange | positions along the lamination direction of a plate-shaped structural member, It is characterized by the above-mentioned.

  The steam injector according to the present invention is characterized in that, in the above-described invention, a flow path is formed which communicates the introduction portions of the unit steam injectors arranged along the laminating direction of the plate-like component members.

  In the steam injector according to the present invention, in the above invention, the set of constituent members are joined to each other in a stacked state, and the plurality of unit steam injectors extend along a stacking direction of the constituent members. It is characterized by.

  The steam injector according to the present invention is characterized in that, in the above invention, the set of constituent members is joined by diffusion joining.

  In the steam injector according to the present invention, in the above invention, the unit steam injector is discharged from the discharge portion of the diffuser portion when the internal cross-sectional area of the throat portion decreases the internal cross-sectional area of the throat portion. The refrigerant flow has a cross-sectional area smaller than a critical cross-sectional area in which the discharge pressure of the refrigerant flow increases nonlinearly.

  In the steam injector according to the present invention, in the above invention, the first-order differential coefficient of the curve representing the change in the discharge pressure of the refrigerant flow with respect to the change in the inner cross-sectional area of the throat portion is 0 The internal cross-sectional area is small or has a second-order differential coefficient greater than 0.

The steam injector according to the present invention is characterized in that, in the above invention, the internal cross-sectional area of the throat portion is A ₁ , the mass flow rate and the flow velocity of the liquid flow in the introduction portion are m _w0 , u _w0 , and the steam flow in the introduction portion, respectively. Mass flow rate and flow velocity of m _s0 and u _s0 , respectively, and mass flow rate and flow velocity of the refrigerant flow in the throat portion respectively m ₁ and u ₁ , and pressure loss coefficients in the mixing portion, throat portion, and diffuser portion, respectively. _{ζ N, ζ T, ζ D} , density [rho _w of the liquid _flow, a discharge pressure at the discharge portion of the refrigerant flow when the P _D, wherein the following formula is valid (1).

  The steam injector according to the present invention is characterized in that, in the above invention, the throat portion has a circular internal cross section, and the internal cross section has a diameter of 2 mm or less.

  The steam injector according to the present invention is characterized in that, in the above invention, the diameter of the internal cross section is 1 mm or less.

The steam injector according to the present invention is characterized in that, in the above-mentioned invention, when the cross-sectional area of the region where the liquid flow is introduced is A _W and the cross-sectional area of the region where the steam flow is introduced is A _S in the mixing unit, A _s0 / _Aw0 is 7 or more and 30 or less.

The steam injector according to the present invention is characterized in that, in the above invention, the A _s0 / A _w0 is 10 or more and 20 or less.

  The steam injector according to the present invention is characterized in that, in the above-described invention, the steam injector further includes a drain pipe formed so as to communicate with the outside air from the inside of the mixing section.

  The steam injector according to the present invention is characterized in that, in the above-mentioned invention, the drain pipe is provided with a check valve.

  In the steam injector according to the present invention, in the above invention, the introduction portion includes a liquid flow introduction portion, a vapor flow introduction portion, and a heat insulating layer interposed between the liquid flow introduction portion and the vapor flow introduction portion. It is characterized by having.

  The steam injector according to the present invention is characterized in that, in the above invention, the refrigerant is water or alternative chlorofluorocarbon.

  In the heat pump device according to the present invention, a compressor that compresses the refrigerant, a condenser that condenses the refrigerant, an evaporator that evaporates the refrigerant, a vapor flow of the refrigerant, and a liquid flow of the refrigerant are introduced. And a steam injector according to the invention described above, which discharges a refrigerant flow whose pressure has been increased from a discharge part of the diffuser part.

  According to the present invention, there is an effect that it is possible to realize a steam injector that is small but has a large discharge amount and a heat pump device using the same.

FIG. 1 is a schematic perspective view of a steam injector according to the first embodiment. FIG. 2 is a plan view of the plate-shaped component of FIG. FIG. 3 is a cross-sectional view of a main part of the steam injector of FIG. FIG. 4 is a diagram for explaining the flow of the refrigerant. FIG. 5 is a cross-sectional view of a main part for explaining another aspect of the introduction part. FIG. 6 is a schematic diagram illustrating the internal configuration of the steam injector according to the first modification. FIG. 7 is a plan view of the plate-like component shown in FIG. FIG. 8 is a plan view of the plate-like component shown in FIG. FIG. 9 is a perspective view of the plate-like component shown in FIG. FIG. 10 is a schematic diagram illustrating the internal configuration of the steam injector according to the second modification. FIG. 11 is a plan view of the plate-like component shown in FIG. FIG. 12 is a plan view of the plate-like component shown in FIG. FIG. 13 is a schematic diagram for explaining the internal configuration of the steam injector according to the third modification. 14 is a plan view of the plate-like component shown in FIG. FIG. 15 is a plan view of the plate-like component shown in FIG. FIG. 16 is a schematic diagram illustrating a configuration of a steam injector according to Modification 4. FIG. 17 is a schematic diagram illustrating the configuration of the plate-like component and the nozzle of FIG. FIG. 18 is a schematic diagram illustrating an internal configuration of a steam injector according to Modification 5. FIG. 19 is a plan view of the plate-like component shown in FIG. FIG. 20 is a plan view of the plate-like component shown in FIG. FIG. 21 is a schematic diagram illustrating an internal configuration of a steam injector according to Modification 6. FIG. 22 is a block diagram of the heat pump device according to the second embodiment. FIG. 23 is a block diagram of the heat pump device according to the third embodiment. FIG. 24 is a diagram for explaining an operational characteristic prediction model of a steam injector. FIG. 25 is a diagram illustrating the relationship between the inner diameter of the throat portion and the discharge pressure. FIG. 26 is a diagram showing first-order differential coefficients of the curve shown in FIG. FIG. 27 is a diagram showing second-order differential coefficients of the curve shown in FIG. FIG. 28 is a diagram illustrating the relationship between the pressure of the vapor flow and the discharge pressure in the introduction section. FIG. 29 is a diagram schematically showing the configuration of the manufactured unit vapor injector. FIG. 30 is a diagram showing the pressure of the steam flow introduced and the pressure in the drain pipe during the stable operation and the unstable operation.

  Hereinafter, embodiments of a steam injector and a heat pump device according to the present invention will be described in detail with reference to the drawings. Note that the present invention is not limited to the embodiments. Moreover, in each drawing, the same code | symbol is attached | subjected suitably to the same or corresponding component. In addition, it should be noted that the drawings are schematic, and the ratio of the dimensions of each element is different from the actual one. Moreover, the part from which the relationship and ratio of a mutual dimension differ also in between drawings is contained.

(Embodiment 1)
FIG. 1 is a schematic perspective view of a steam injector according to the first embodiment. This steam injector 100 is composed of a plurality (5 in the first embodiment) of plate-like constituent members 101, 102, 103, 104, and 105. The set of plate-like constituent members 101, 102, 103, 104, and 105 are joined to each other in a stacked state. The plate-like constituent members 101 and 105 constitute the uppermost layer or the lowermost layer of the steam injector 100 having a laminated structure.

  The plate-like component 101 is formed with a refrigerant liquid supply port 101a for supplying the refrigerant liquid flow W1 from the outside and a refrigerant vapor discharge port 101b for discharging the refrigerant vapor flow S1 to the outside. The plate-like component 105 is formed with a refrigerant liquid discharge port 105a for discharging the liquid flow W1 to the outside and a refrigerant vapor supply port 105b for supplying the vapor flow S1 from the outside. In addition, a refrigerant flow discharge port 106 for discharging the refrigerant flow F <b> 1 is formed on the side surface of the vapor injector 100.

  FIG. 2 is a plan view of the plate-like component 102. In FIG. 2, the hatched portion is the main surface of the plate-like component member 102, and a plurality of grooves and holes are formed on the main surface of the plate-like component member 102. These grooves and holes are the plate-like components of the plate-like component member 101, the main surface of the plate-like member 102 facing the plate-like component member 102, the two main surfaces of the plate-like component members 102, 103, and 104, It is also formed on the main surface facing the member 104. These grooves and holes include a groove or a hole having a shape obtained by dividing an introduction portion, a mixing portion, a throat portion, and a diffuser portion of a unit steam injector, which will be described later, into plate-like constituent members 101, 102, 103, 104, 105. By joining the main surfaces facing each other, these grooves or holes are combined to provide a plurality of unit vapor injectors and a flow path for supplying or discharging refrigerant liquid and refrigerant vapor to the unit vapor injectors Is formed.

  Specifically, as shown in FIG. 2, the plate-shaped component 102 is formed with a refrigerant liquid supply port 102a, a refrigerant vapor discharge port 102b, a refrigerant liquid discharge port 102c, and a refrigerant vapor supply port 102d. ing. Further, by joining the plate-like member 102 and the plate-like member 103, three unit vapor injectors 10, a refrigerant liquid channel 102e, a refrigerant vapor channel 102f, and a refrigerant flow merge channel 102g are formed. The The refrigerant liquid supply port 102a communicates with the refrigerant liquid supply port 101a shown in FIG. The refrigerant vapor outlet 102b communicates with the refrigerant vapor outlet 101b shown in FIG. The refrigerant liquid outlet 102c communicates with the refrigerant liquid outlet 105a shown in FIG. The refrigerant vapor supply port 102d communicates with the refrigerant vapor supply port 105b shown in FIG. The refrigerant liquid supply port 102a and the refrigerant liquid discharge port 102c communicate with each other via the refrigerant liquid flow path 102e. The refrigerant vapor discharge port 102b and the refrigerant vapor supply port 102d communicate with each other via a refrigerant vapor channel 102f.

  The unit steam injectors 10 are arranged along the main surfaces of the plate-like constituent members 101 and 102. Further, since the unit steam injector 10 is formed between the respective plate-like constituent members by joining a pair of plate-like constituent members 101, 102, 103, 104, 105, the plate-like constituent members 101, 102, 103 are formed. , 104, 105 are also arranged along the stacking direction. In the steam injector 100, three unit steam injectors are formed along the main surface and four along the stacking direction. Therefore, the steam injector 100 is a total of 12 unit steam injectors. When the number of unit steam injectors arranged along the main surface or the stacking direction is N and M, respectively, in the case of the steam injector 100, N = 3 and M = 4, but N is 1 and M is 2 As described above, N may be 2 or more, M may be 1, or N and M may be 2 or more.

  Each unit steam injector 10 includes an introduction part 1, a mixing part 2, a throat part 3, and a diffuser part 4. Hereinafter, the configuration and operation of the unit steam injector 10 will be described.

  The introduction part 1 has a nozzle-like liquid flow introduction part 1a and a vapor flow introduction part 1b. The liquid flow introduction unit 1a introduces a refrigerant liquid flow W1 supplied from the outside through the refrigerant liquid supply port 101a, the refrigerant liquid supply port 102a, and the refrigerant liquid channel 102e. The vapor flow introducing portion 1b is formed on both sides of the liquid flow introducing portion 1a, and introduces the vapor flow S1 supplied via the refrigerant vapor supply port 105b, the refrigerant vapor supply port 102d, and the refrigerant vapor channel 102f. The liquid flow W1 is introduced in the form of a jet by the nozzle-shaped liquid flow introducing portion 1a. In addition, if the refrigerant | coolant to be used is a refrigerant | coolant which can be used with a heat pump apparatus, such as water and a substitute Freon, it will not specifically limit.

  FIG. 3 is a cross-sectional view of a main part of the steam injector 100, showing a cross section in a cross section corresponding to the line AA in FIG. Thus, the liquid flow introducing portion 1a and the vapor flow introducing portion 1b are formed by combining the grooves formed on the opposing main surfaces when the plate-like component member 101 and the plate-like component member 102 are joined. The

  Returning to FIG. The mixing unit 2 has a shape in which the internal cross-sectional area decreases toward the traveling direction of the liquid flow, which is the right side of FIG. In the first embodiment, the mixing unit 2 has a rectangular cross section, but may have another shape such as a circular cross section. The mixing unit 2 is a part that mixes the liquid flow and the vapor flow inside to form a refrigerant flow in a gas-liquid mixed state. Here, the vapor flow is rapidly cooled and condensed by the liquid flow, and its volume is greatly reduced, so that a negative pressure is generated inside the mixing unit 2. This also increases the flow rate of the steam flow introduced.

  As shown in FIG. 2, the vapor flow S1 introduced from the liquid flow introduction portion 1a is merged with and mixed with the liquid flow W1 from the outer peripheral side of the jet-like liquid flow W1 introduced from the vapor flow introduction portion 1b. .

  The throat section 3 is formed on the output side of the mixing section 2 and on the input side of the diffuser section 4. In the first embodiment, the throat portion 3 has a rectangular cross section, but may have another shape such as a circular cross section. The throat portion 3 is a portion extending from the mixing portion 2 to the diffuser portion 4 and having the smallest internal cross-sectional area. Therefore, the refrigerant flow has the highest flow velocity when passing through the throat portion 3.

  The diffuser part 4 has a shape in which the internal cross-sectional area increases from the throat part 3 toward the traveling direction of the refrigerant flow. In the first embodiment, the diffuser portion 4 has a rectangular cross section, but may have another shape such as a circular cross section. Since the internal cross-sectional area of the diffuser portion 4 is enlarged, the flow rate of the refrigerant flow is reduced and the pressure is increased. As a result, the diffuser unit 4 discharges the refrigerant flow whose pressure is increased from the discharge unit 4a as the refrigerant flow F1.

  The refrigerant flow merging flow path 102g communicates with the discharge portion of the diffuser portion of each unit vapor injector 10, and merges the discharged refrigerant flows F1. The refrigerant flow outlet 106 discharges the merged refrigerant flow F <b> 1 to the outside of the vapor injector 100.

  FIG. 4 is a diagram for explaining the flow of the refrigerant. As shown in FIG. 4, the refrigerant liquid flow W <b> 1 is supplied from the refrigerant liquid supply port 101 a, and then from the refrigerant liquid supply port formed in the plate-like component member 102, the plate-like component member 101 and the plate-like component member. The unit steam injectors formed by joining with 102 are supplied. The liquid flow that has not been supplied to each unit vapor injector is discharged from the refrigerant liquid discharge port, and is joined to the plate-shaped component member 102 and the plate-shaped component member 103 from the refrigerant liquid supply port formed in the plate-shaped component member 103. It is supplied to each unit steam injector formed. In other words, the refrigerant liquid supply port and the refrigerant liquid discharge port of the adjacent plate-shaped component members are in communication with each other, and a flow path that communicates each introduction portion of the unit steam injectors arranged along the stacking direction of the plate-shaped component members. Forming. Hereinafter, similarly, a liquid flow is supplied to each unit steam injector formed by joining the respective plate-shaped component members, and an unused liquid flow is discharged to the outside from the refrigerant liquid discharge port 105a of the plate-shaped component member 105. .

  Similarly, the refrigerant vapor flow S <b> 1 is supplied from the refrigerant vapor supply port 105 b and then joined to the plate-like component member 105 and the plate-like component member 104 from the refrigerant vapor supply port formed in the plate-like component member 104. Is supplied to each unit steam injector formed. The vapor flow that has not been supplied to each unit vapor injector is discharged from the refrigerant vapor discharge port, and the plate-like component member 104 and the plate-like component member 103 are joined from the refrigerant vapor supply port formed in the plate-like component member 103. It is supplied to each unit steam injector formed. Hereinafter, similarly, a steam flow is supplied to each unit steam injector formed by joining each plate-shaped component, and the unused steam flow is discharged to the outside from the refrigerant vapor discharge port 101b of the plate-shaped component 101. .

  The steam injector 100 is an assembly of 12 unit steam injectors as described above, and discharges a refrigerant flow that combines all of the refrigerant flows discharged by the unit steam injectors. Therefore, this steam injector is small and has a large discharge amount.

  In addition, FIG. 5 is a principal part sectional view explaining another aspect of the introduction part. As shown in FIG. 5, the introduction part 1 ′ can be used in place of the introduction part 1 shown in FIGS. 2 and 3, and is interposed between the liquid flow introduction part 1a and the vapor flow introduction part 1b. It has the heat insulation layer 1c. The heat insulation layer 1c can be configured, for example, as a layer filled with air between two wall portions or a vacuum layer.

  When the liquid flow W1 is heated by the vapor flow S1 in the introduction part 1, the effect of rapidly cooling and condensing the vapor flow S1 in the mixing part 2 by the liquid flow W1 decreases. On the other hand, in the introduction part 1 ′, the heat insulating layer 1 c prevents or suppresses the liquid flow W <b> 1 from being heated by the vapor flow S <b> 1, thereby preventing or suppressing the decrease in the condensation effect.

  The plate-like constituent members 101, 102, 103, 104, and 105 may be made of, for example, a resin material. These are made of metal or the like, and a set of plate-like constituent members are joined by diffusion bonding or the like. As a result, the discharge amount of the refrigerant flow F1 is large, and sufficient bonding strength can be obtained even if the discharge thickness is high. As a metal material which comprises a plate-shaped structural member, what has high heat insulation, such as stainless steel material, is preferable.

  The unit steam injector 10 may further include a drain pipe formed to communicate with the outside air from the inside of the mixing unit 2. The drain pipe has a function of exhausting excess steam in the mixing unit 2. By exhausting excess steam in this way, the operation stability of the unit steam injector 10 is increased. The drain pipe may be provided with a check valve. When the unit steam injector 10 operates, a negative pressure is generated inside the mixing unit 2 as described above. The check valve functions to prevent outside air from flowing into the mixing unit 2 due to negative pressure, thereby increasing the stability of the operation of the unit steam injector 10.

  Hereinafter, the injectors according to the first to sixth modifications of the first embodiment will be described.

(Modification 1)
FIG. 6 is a schematic diagram illustrating the internal configuration of the steam injector according to the first modification. FIG. 6A shows a steam injector 100A, and FIGS. 6B, 6C, and 6D show plate-like constituent members 102A, 103A, and 101A that are constituent elements thereof. The steam injector 100A has a configuration in which a plurality of sets of plate-like component members 101A arranged between a plurality of plate-like component members 102A and 103A are stacked. These plate member constituent members are made of metal, for example, and are joined by diffusion bonding.

  FIG. 7 is a plan view of the plate-like component 102A of FIG. In FIG. 7, the area | region where the cross hatching was given has shown the groove | channel. The plate-like component 103A has the same configuration as the plate-like member 102A. As shown in FIG. 7, the plate-like component 102A includes a refrigerant liquid channel 102Ae, a refrigerant vapor channel 102Af, a refrigerant flow merge channel 102Ag, and a refrigerant flow so as to penetrate the plate-like member 102A. A discharge port 106A is formed. Further, the plate-like component 102A has grooves for constituting the introduction part 1A, the mixing part 2A, the throat part 3A, and the diffuser part 4A of the unit steam injector 10A. A unit steam injector 10A is formed by joining the plate-like member 102A and the plate-like member 103A. The plate-like component 102A and the plate-like member 103A may be laminated so that the grooves are combined with each other, the main surface on which the groove of one plate-like component is formed, and one plate-like member You may laminate | stack so that the main surface in which the groove | channel of a structural member is not formed may oppose.

  Each unit steam injector 10A includes an introduction part 1A, a mixing part 2A, a throat part 3A, and a diffuser part 4A. The introduction unit 1A includes a nozzle-like liquid flow introduction unit 1Aa and a vapor flow introduction unit 1Ab. The liquid flow introduction unit 1Aa introduces a liquid flow of the refrigerant supplied from the outside via the refrigerant liquid flow path 102Ae. The vapor flow introduction part 1Ab is formed on both sides of the liquid flow introduction part 1Aa, and introduces the vapor flow supplied via the refrigerant vapor flow path 102Af. The specific configuration and operation of the unit steam injector 10A are substantially the same as those of the unit steam injector 10.

  FIG. 8 is a plan view of the plate-like component 101A shown in FIG. As shown in FIG. 8, in the plate-shaped component 101A, a refrigerant liquid channel 101Ae, a refrigerant vapor channel 101Af, a refrigerant flow merging channel 101Ag, and a refrigerant flow discharge port 106A are formed. The plate-shaped component 101A is sandwiched between the plate-shaped component 102A and the plate-shaped component 103A, and a spacer for securing a flow path of the refrigerant vapor to the vapor flow introducing portion 1Ab of each unit vapor injector 10A. It plays the role of

  FIG. 9 is a perspective view of the plate-like component 102A shown in FIG. 6, and shows the plate-like member 102A cut for easy understanding of the groove configuration.

(Modification 2)
FIG. 10 is a schematic diagram illustrating the internal configuration of the steam injector according to the second modification. FIG. 10A shows a steam injector 100B, and FIGS. 10B, 10C, and 10D show plate-like constituent members 102B, 103B, and 101B that are constituent elements thereof. The steam injector 100B has a configuration in which a plurality of sets of plate-shaped component members 101B arranged between a plurality of plate-shaped component members 102B and 103B are stacked. These plate member constituent members are made of metal, for example, and are joined by diffusion bonding.

  FIG. 11 is a plan view of the plate-like component 102B of FIG. In FIG. 11, the area | region where the cross hatching was given has shown the groove | channel. The plate-like component 103B has the same configuration as the plate-like member 102B. As shown in FIG. 11, the plate-like component 102B includes a refrigerant liquid channel 102Be, a refrigerant vapor channel 102Bf, a refrigerant flow merge channel 102Bg, and a refrigerant flow so as to penetrate the plate-like member 102B. A discharge port 106B is formed. Further, the plate-like component 102B has grooves for constituting the introduction part 1B, the mixing part 2B, the throat part 3B, and the diffuser part 4B of the unit steam injector 10B. A unit steam injector 10B is formed by joining the plate-like member 102B and the plate-like member 103B. In addition, the plate-like component member 102B and the plate-like component member 103B may be laminated so that the grooves are combined with each other, the main surface on which the groove of one plate-like component member is formed, and one plate-like member You may laminate | stack so that the main surface in which the groove | channel of a structural member is not formed may oppose.

  Each unit steam injector 10B includes an introduction part 1B, a mixing part 2B, a throat part 3B, and a diffuser part 4B. The introduction part 1B has a nozzle-like liquid flow introduction part 1Ba and a vapor flow introduction part 1Bb. The liquid flow introduction unit 1Ba introduces a liquid flow of the refrigerant supplied from the outside via the refrigerant liquid flow path 102Be. The vapor flow introduction part 1Bb is formed on both sides of the liquid flow introduction part 1Ba, and introduces the vapor flow supplied via the refrigerant vapor flow path 102Bf. The specific configuration and operation of the unit steam injector 10B are substantially the same as those of the unit steam injector 10.

  FIG. 12 is a plan view of the plate-like component 101B of FIG. As shown in FIG. 12, the plate-like component 101B is formed with a refrigerant liquid channel 101Be, a refrigerant vapor channel 101Bf, a refrigerant flow merge channel 101Bg, and a refrigerant flow discharge port 106B. The plate-like member 101B is sandwiched between the plate-like member 102B and the plate-like member 103B, and a spacer for securing a flow path of the refrigerant vapor to the vapor flow introduction portion 1Bb of each unit vapor injector 10B. It plays the role of

  Here, the plate-like component 102B is further formed with a through groove 1Bc interposed between the liquid flow introduction portion 1Ba and the vapor flow introduction portion 1Bb. Such a through groove 1Bc is also formed in the plate-like component 101B. Further, the through groove 1Bc is formed so as to be interposed between the refrigerant liquid channel 102Be and the refrigerant vapor channel 102Bf. This through groove 1Bc forms an air layer as a heat insulating layer that insulates between the liquid flow introducing portion 1Ba and the vapor flow introducing portion 1Bb and between the refrigerant liquid flow channel 102Be and the refrigerant vapor flow channel 102Bf. Accordingly, the liquid flow is prevented or suppressed from being heated by the vapor flow before mixing, so that the reduction of the condensation effect in the mixing unit 2B is prevented or suppressed. The through groove 1Bc may be evacuated.

(Modification 3)
FIG. 13 is a schematic diagram for explaining the internal configuration of the steam injector according to the third modification. FIG. 13A shows a steam injector 100C, and FIGS. 13B, 13C, and 13D show plate-like constituent members 102C, 103C, and 101C that are constituent elements thereof. The steam injector 100C has a configuration in which a plurality of plate-like component members 101C arranged between a plurality of plate-like component members 102C and 103C are stacked. These plate member constituent members are made of metal, for example, and are joined by diffusion bonding.

  FIG. 14 is a plan view of the plate-like component 102C of FIG. In FIG. 14, the area | region where the cross hatching was given has shown the groove | channel. The plate-like component 103C has the same configuration as the plate-like member 102C. As shown in FIG. 14, the plate-like component 102C includes a refrigerant liquid channel 102Ce, a refrigerant vapor channel 102Cf, a refrigerant flow merge channel 102Cg, and a refrigerant flow so as to penetrate the plate-like member 102C. A discharge port 106C is formed. Further, the plate-like component member 102C has grooves for constituting the introduction part 1C, the mixing part 2C, the throat part 3C, and the diffuser part 4C of the unit steam injector 10C. A unit steam injector 10C is formed by joining the plate-like member 102C and the plate-like member 103C. The plate-like component member 102C and the plate-like component member 103C may be laminated so that the grooves are combined with each other, the main surface on which the groove of one plate-like component member is formed, and one plate-like member You may laminate | stack so that the main surface in which the groove | channel of a structural member is not formed may oppose.

  Each unit steam injector 10C includes an introduction part 1C, a mixing part 2C, a throat part 3C, and a diffuser part 4C. The introduction part 1C has a nozzle-like liquid flow introduction part 1Ca and a vapor flow introduction part 1Cb. The liquid flow introduction unit 1Ca introduces a liquid flow of the refrigerant supplied from the outside via the refrigerant liquid flow path 102Ce. The vapor flow introduction part 1Cb is formed on both sides of the liquid flow introduction part 1Ca, and introduces the vapor flow supplied via the refrigerant vapor flow path 102Cf. The specific configuration and operation of the unit steam injector 10C are substantially the same as those of the unit steam injector 10. In the unit steam injector 10C, the steam flow is mixed from the side surface in the liquid flow traveling direction. In FIG. 14, reference numeral 1Caa indicates a cross-sectional area into which a liquid flow is introduced during mixing, and reference numeral 1Cba indicates a cross-sectional area into which a vapor flow is introduced during mixing.

  FIG. 15 is a plan view of the plate-like component 101C of FIG. As shown in FIG. 15, a refrigerant liquid channel 101Ce, a refrigerant vapor channel 101Cf, a refrigerant flow merging channel 101Cg, and a refrigerant flow discharge port 106C are formed in the plate-shaped component 101C. The plate-like member 101C is sandwiched between the plate-like member 102C and the plate-like member 103C, and is a spacer for securing a flow path of the refrigerant vapor to the steam flow introducing portion 1Cb of each unit steam injector 10C. It plays the role of

  Here, similarly to the plate-like component 102B, the plate-like member 102C is also formed with a through groove 1Cc interposed between the liquid flow introduction portion 1Ca and the vapor flow introduction portion 1Cb. Such a through groove 1Cc is also formed in the plate-like component 101C. Further, the through groove 1Cc is formed so as to be interposed between the refrigerant liquid channel 102Ce and the refrigerant vapor channel 102Cf. This through groove 1Cc forms an air layer as a heat insulating layer that insulates between the liquid flow introducing portion 1Ca and the vapor flow introducing portion 1Cb and between the refrigerant liquid flow channel 102Ce and the refrigerant vapor flow channel 102Cf. Accordingly, since the liquid flow is prevented or suppressed from being heated by the vapor flow before mixing, the reduction of the condensation effect in the mixing unit 2C is prevented or suppressed. The through groove 1Cc may be evacuated.

(Modification 4)
FIG. 16 is a schematic diagram illustrating an internal configuration of a steam injector according to Modification 4. FIG. 16A shows a steam injector 100D, and FIGS. 16B, 16C, and 16D show a plate-like component member 102D, a nozzle 110D, and a plate-like component member 103D, which are components thereof. The steam injector 100D has a configuration in which a plurality of sets of plate-like component members 102D and 103D are stacked. These plate member constituent members are made of metal, for example, and are joined by diffusion bonding.

  FIG. 17 is a schematic diagram illustrating the configuration of the plate-like component and the nozzle of FIG. 17A shows a plate-like component 102D, FIGS. 17B and 17C show a rear view and a side view, respectively, and FIGS. 17D, 17E and 17F show A- A cross section taken along the line A, a cross section taken along the line BB, and a cross section taken along the line C-C are shown, and FIG. In FIG. 17, the area | region where the cross hatching was given has shown the groove | channel. The plate-like component 103D has the same configuration as the plate-like member 102D.

  As shown in FIG. 17, the plate-like component 102D includes a refrigerant liquid channel 102De, a refrigerant vapor channel 102Df, a refrigerant flow merge channel 102Dg, and a refrigerant flow so as to penetrate the plate-like member 102D. A discharge port 106D is formed. In addition, the plate-like component 102D has grooves for constituting the mixing portion 2D, the throat portion 3D, and the diffuser portion 4D of the unit steam injector 10D. Furthermore, the plate-like component 102D has a groove 102Dh for fitting the nozzle 110D. A unit steam injector 10D is formed by joining the plate-like component 102D and the plate-like component 103D with the nozzle 110D fitted in the groove 102Dh. At this time, the nozzle 110D fits into a groove similar to the groove 102Dh formed on the plate-like component 103D side.

  Each unit steam injector 10D includes an introduction part 1D, a mixing part 2D, a throat part 3D, and a diffuser part 4D. The introduction unit 1D includes a nozzle-like liquid flow introduction unit 1Da and a vapor flow introduction unit 1Db. The liquid flow introduction unit 1Da introduces the liquid flow of the refrigerant supplied from the outside via the refrigerant liquid flow channel 102De. The vapor flow introduction unit 1Db is formed so as to surround the liquid flow introduction unit 1Da, and introduces the vapor flow supplied via the refrigerant vapor channel 102Df. The specific configuration and operation of the unit steam injector 10D are substantially the same as those of the unit steam injector 10.

  Here, when the plate-like component 102D and the plate-like component 103D are joined with the nozzle 110D fitted in the groove 102Dh, the liquid flow introduction portion 1Da of the introduction portion 1D is formed by the nozzle 110D, and the mixing portion 2D A groove surrounding the periphery of the nozzle 110D in the refrigerant vapor flow path 102Df serves as the vapor flow introduction portion 1Db. The steam injector 100D has a mechanism that allows the nozzle 110D to move in the groove 102Dh and to be fixed at a desired position. By moving the position of the nozzle 110D with respect to the longitudinal direction of the groove 102Dh, the cross-sectional area ratio between the liquid flow introduction part 1Da and the vapor flow introduction part 1Db in the introduction part 1D can be changed.

(Modification 5)
FIG. 18 is a schematic diagram illustrating an internal configuration of a steam injector according to Modification 5. FIG. 18A shows a steam injector 100E, and FIGS. 18B, 18C, 18D, and 18E show plate-like constituent members 102E, 103E, 104E, and 101E that are constituent elements thereof. . The steam injector 100E has a configuration in which a plurality of sets of plate-like constituent members 102E, 103E, 104E, and 101E are stacked. These plate member constituent members are made of metal, for example, and are joined by diffusion bonding.

  FIG. 19 is a plan view of the plate-like component 103E of FIG. In FIG. 19, the area | region where the cross hatching was given has shown the groove | channel. The plate-like component 104E has the same configuration as the plate-like member 103E. As shown in FIG. 19, the plate-like component 103E includes a refrigerant liquid channel 103Ee, a refrigerant vapor channel 103Ef, a refrigerant flow merge channel 103Eg, and a refrigerant flow so as to penetrate the plate-like member 103E. A discharge port 106E is formed. Further, the plate-like component 103E has grooves for constituting the introduction part 1E, the mixing part 2E, the throat part 3E, and the diffuser part 4E of the unit steam injector 10E. Further, a wedge-shaped through-hole penetrating the plate-like component 103E is formed in the plate-like member 103E so as to constitute the steam flow introduction portion 1Ec.

  FIG. 20 is a plan view of the plate-like component 102E of FIG. The plate-like component 101E has the same configuration as the plate-like member 102E. As shown in FIG. 20, a refrigerant liquid channel 102Ee, a refrigerant vapor channel 102Ef, a refrigerant flow merging channel 102Eg, and a refrigerant flow outlet 106E are formed in the plate-like component 102E. Further, the plate-like component 102E constitutes a groove that constitutes the steam flow introduction part 1Ec, a groove that constitutes the throat part 3E, and a flow path 102Eh that allows the refrigerant vapor to escape, communicating with the refrigerant vapor flow path 102Ef. And a groove for the purpose. In addition, the groove | channel for comprising the flow path 102Eh which escapes refrigerant | coolant vapor | steam may not be provided.

  The unit steam injector 10E is formed by joining the plate-like structural members 102E, 103E, 104E, and 101E. In addition, in order to configure the steam flow introducing portion 1Ec formed in the plate-shaped component 102E and the through hole for configuring the steam flow introducing portion 1Ec formed in the plate-shaped component 103E when joined. It communicates with the groove. The plate-like component member 104E and the plate-like component member 101E are also formed with similar through holes and grooves, which communicate when joined.

  Each unit steam injector 10E includes an introduction part 1E, a mixing part 2E, a throat part 3E, and a diffuser part 4E. The introduction part 1E has a nozzle-like liquid flow introduction part 1Ea and vapor flow introduction parts 1Eb, 1Ec. The liquid flow introduction unit 1Ea introduces a liquid flow of the refrigerant supplied from the outside via the refrigerant liquid flow path 103Ee. The vapor flow introduction part 1Eb is formed on both sides of the liquid flow introduction part 1Ea, and introduces the vapor flow supplied via the refrigerant vapor flow path 103Ef.

  Further, the steam flow introduction portion 1Ec is formed above and below the liquid flow introduction portion 1Ea, and is a groove constituting the steam flow introduction portion 1Ec formed in the plate-like constituent members 102E and 101E from the refrigerant vapor flow path (see FIG. 20). ), And the steam flow supplied through the through holes (see FIG. 19) constituting the steam flow introduction part 1Ec formed in the plate-like structural members 103E and 104E is introduced. That is, in each unit steam injector 10E, the steam flow is introduced from the left and right sides of the liquid flow introduction portion 1Ea and from the upper and lower sides. In addition, although it passed the groove | channel which comprises the steam flow introduction part 1Ec formed in plate-shaped structural member 102E, 101E, it did not pass the hole which comprises the steam flow introduction part 1Ec formed in plate-shaped structural member 103E, 104E. The refrigerant vapor is released from the flow path 102Eh to the refrigerant flow outlet 106E.

  Other specific configurations and operations of the unit steam injector 10E are substantially the same as those of the unit steam injector 10. In this unit vapor injector 10E, the refrigerant vapor is introduced from the vapor flow introduction portions 1Eb and 1Ec formed on the four sides of the liquid flow introduction portion 1Ea, so that the refrigerant vapor can be introduced more efficiently.

(Modification 6)
FIG. 21 is a schematic diagram illustrating an internal configuration of a steam injector according to Modification 6. The steam injector 200 includes constituent members 201, 202, 203, 204, and 205. By laminating and joining the constituent members 201, 202, 203, 204, and 205, nine unit steam injectors 10G extending along the stacking direction of the constituent members 201, 202, 203, 204, and 205 are formed. The Each unit steam injector 10G includes an introduction part 1G, a mixing part 2G, a throat part 3G, and a diffuser part 4G. The introduction part 1G has a nozzle-like liquid flow introduction part 1Ga and a vapor flow introduction part 1Gb. These constituent members are made of metal, for example, and are joined by diffusion bonding.

  The constituent member 201 has a refrigerant liquid flow path 200e which is a through hole having a rectangular cross section. In addition, the constituent member 201 includes a refrigerant liquid flow path 200e and a communication hole 200e1 communicating with the liquid flow introducing portion 1Ga of the introducing portion 1G formed by the constituent member 205 that is a nozzle. The constituent member 202 is formed with a mixing portion 2G which is a conical through hole. Further, when the constituent members 201, 202, and 205 are joined, the constituent member 201 and the constituent member 202 form a refrigerant vapor channel 200 f. In addition, the component member 205 is inserted into the mixing unit 2G, and the steam flow introduction unit 1Gb is formed in the gap between the component member 205 and the mixing unit 2G.

  Further, the component member 203 is formed with a diffuser portion 4G which is a conical through hole. When the constituent member 202 and the constituent member 203 are joined, the throat portion 3G is formed at the position of the joining surface between the constituent member 202 and the constituent member 203. Further, when the constituent member 203 and the constituent member 204 are joined, the refrigerant flow merge channel 200g and the refrigerant flow discharge port 206 are formed.

  Thus, the unit steam injector may be formed so as to extend along the stacking direction of the constituent members to be stacked and joined.

(Embodiment 2)
FIG. 22 is a block diagram of a heat pump apparatus according to Embodiment 2 of the present invention. As shown in FIG. 22, the heat pump apparatus 1000 includes the steam injector 100 according to the first embodiment, the compressor 20, the condenser 30, the evaporator 40, and the gas-liquid separator 50. These elements are connected by piping as a flow path for circulating the refrigerant.

  The operation of the heat pump apparatus 1000 will be described. The compressor 20 compresses the refrigerant vapor supplied from the gas-liquid separator 50 with the electric power P from the outside. On the other hand, the condenser 30 radiates the heat of the compressed refrigerant vapor as heat H1 and condenses the refrigerant vapor to obtain a refrigerant liquid. The evaporator 40 evaporates the refrigerant by applying heat H2 absorbed from the outside to the refrigerant liquid supplied from the gas-liquid separator 50.

  The vapor injector 100 introduces the refrigerant vapor flow supplied from the evaporator 40 and the refrigerant liquid flow supplied from the condenser 30 into the refrigerant flow discharge port 106 (FIG. 1). (Refer to). The gas-liquid separator 50 separates the liquid and vapor of the refrigerant contained in the discharged refrigerant flow, supplies the refrigerant vapor to the compressor 20, and supplies the refrigerant liquid to the evaporator 40.

  In the heat pump apparatus 1000, the steam injector 100 can recover the energy lost as a vortex in the expansion valve in the heat pump apparatus using the expansion valve. Furthermore, in this heat pump apparatus 1000, since the burden on the compressor 20 is reduced by the steam injector 100, the amount of electric power P to be applied from the outside in order to realize a desired operation state can be reduced. As a result, the heat pump apparatus 1000 functions as a high-efficiency heat pump apparatus with improved COP. The heat pump device 1000 can be used for various devices using the heat pump device such as an air conditioner, a refrigeration device, and a hot water supply device, thereby realizing a high efficiency device.

(Embodiment 3)
FIG. 23 is a block diagram of a heat pump apparatus according to Embodiment 3 of the present invention. As shown in FIG. 23, the heat pump device 2000 includes a steam injector 100 according to the first embodiment, a compressor 20, a condenser 30, an evaporator 40, a gas-liquid separator 50, an expansion valve 60, And a pump 70. These elements are connected by piping as a flow path for circulating the refrigerant.

  In this heat pump device 2000, the steam injector 100 introduces a refrigerant vapor flow supplied from the compressor 20 and a refrigerant liquid flow supplied in a state where the pressure is increased by the pump 70 from the gas-liquid separator 50. Then, the refrigerant flow whose pressure is increased is discharged from the refrigerant flow discharge port 106. The condenser 30 is supplied with the refrigerant flow whose pressure is increased from the vapor injector 100, dissipates the heat as heat H1, and condenses the refrigerant flow. The gas-liquid separator 50 separates the liquid and vapor of the refrigerant contained in the refrigerant flow from the condenser 30, supplies the refrigerant vapor to the expansion valve 60, and supplies the refrigerant liquid to the pump 70. The expansion valve 60 uses the refrigerant vapor as a low-temperature and low-pressure refrigerant liquid. The evaporator 40 evaporates the refrigerant by applying heat H2 absorbed from the outside to the refrigerant liquid that has been reduced in temperature and pressure by the expansion valve 60. The compressor 20 compresses the refrigerant vapor supplied from the evaporator 40 with electric power P from the outside.

  In this heat pump device 2000, the vapor injector 100 assists the compression of the refrigerant by the compressor 20 and supplies the refrigerant with a desired pressure to the condenser 30. As a result, it is possible to reduce the amount of power P to be applied from the outside in order to realize a desired operation state. Thus, the heat pump device 2000 functions as a high-efficiency heat pump device with improved COP. The heat pump device 2000 can be used for various devices using the heat pump device such as an air conditioner, a refrigeration device, and a hot water supply device, thereby realizing a high efficiency device.

  By the way, in consideration of application to a heat pump apparatus such as the above-described refrigeration cycle, it is preferable to use a steam injector having a higher discharge pressure in order to improve energy efficiency represented by COP or the like. The present inventors diligently studied to realize a steam injector having a higher discharge pressure.When the area of the throat portion becomes a predetermined value or less, the discharge pressure of the jet liquid flow to be discharged rapidly increases. I discovered it for the first time.

  For example, in the steam injector 100 according to the first embodiment, the internal cross-sectional area of the throat portion 3 in the unit steam injector 10 is set to be smaller than a predetermined critical cross-sectional area, thereby discharging from the discharge portion 4a of the diffuser portion 4. The discharge pressure of the refrigerant flow is increased.

Hereinafter, the principle of increasing the discharge pressure of the refrigerant flow will be described based on an operational characteristic prediction model of a steam injector (see Non-Patent Document 3). FIG. 24 is a diagram for explaining an operational characteristic prediction model of a steam injector. In FIG. 24, the symbol “0” indicates the start point of the region where the liquid flow W1 and the vapor flow S1 are mixed. Reference C1 indicates a region where the liquid flow W1 is introduced and mixed with the vapor flow S1. The cross-sectional area of this region C1 is _Aw0 . Reference C2 indicates a region where the steam flow S1 is introduced and mixed with the liquid flow W1. The cross-sectional area of this region C2 is assumed to be _As0 . Reference numeral “1” indicates the throat portion 3. Reference sign “D” indicates the discharge section 4 a of the diffuser section 4. These symbols are used as subscripts of variables as appropriate in the following equations.

  In this model, first, it is assumed that the vapor flow S1 is fully condensed in the throat section 3. Further, assuming that the vapor flow S1 becomes a critical flow and is introduced into the mixing unit 2, the flow velocity of the vapor flow S1 is calculated from the critical pressure. Furthermore, the flow structure and the interfacial behavior of the refrigerant flow are not considered.

  First, the mass conservation law equation, the energy conservation law equation, and the momentum conservation side equation are applied to the liquid flow W1, the vapor flow S1, and the refrigerant flow F1 in the mixing unit 2 (between “0” and “1”). . Further, Bernoulli's equation is applied to the refrigerant flow F1 in the diffuser section 4 (between “1” and “D”). This leads to the following formula (1). Here, the refrigerant is water. That is, the values of the water flow and the water vapor flow were used as the parameter values relating to the liquid flow and the vapor flow.

ここで、式（１）では、スロート部３の内部断面積をＡ_１、導入部１における液流Ｗ１の質量流量、流速をそれぞれｍ_ｗ０、ｕ_ｗ０、導入部１における蒸気流Ｓ１の質量流量、流速をそれぞれｍ_ｓ０、ｕ_ｓ０、スロート部３における冷媒流Ｆ１の質量流量、流速をそれぞれｍ_１、ｕ_１、混合部２、スロート部３、ディフューザ部４における圧力損失係数をそれぞれζ_Ｎ、ζ_Ｔ、ζ_Ｄ、液流Ｗ１の密度をρ_ｗ、冷媒流Ｆ１の吐出部４ａにおける吐出圧をＰ_Ｄとしている。また、式（１）を導出する際には、Ａ_ｗ０を７．５４×１０^−７ｍ^２とし、Ａ_ｓ０を５．４２×１０^−６ｍ^２とした。このとき、Ａ_ｓ０／Ａ_ｗ０は約７．２である。また、導入部１における液流Ｗ１の温度Ｔ_ｗ０を２０℃とし、ζ_ｓを０．３７とした。

Here, in Equation (1), the internal cross-sectional area of the throat portion 3 is A ₁ , the mass flow rate of the liquid flow W1 in the introduction portion 1 and the flow velocity are m _w0 and u _w0 , respectively, and the mass flow rate of the vapor flow S1 in the introduction portion 1 , _{M s0} , u _s0 , respectively, the mass flow rate of the refrigerant flow F1 in the throat part 3, and m ₁ , u ₁ , the mixing part 2, the throat part 3 and the pressure loss coefficient in the diffuser part 4 respectively ζ _N , ζ _T, ζ _D, density [rho _w liquid flow W1, the discharge pressure in the discharge section 4a of the refrigerant flow F1 is set to _{P D.} Moreover, when deriving Formula (1), _Aw0 was set to 7.54 × 10 ⁻⁷ m ² and A _s0 was set to 5.42 × 10 ⁻⁶ m ² . At this time, A _s0 / A _w0 is about 7.2. Moreover, the temperature _Tw0 of the liquid flow W1 in the introduction part 1 was set to 20 ° C., and ζ _s was set to 0.37.

In equation (1), ζ _N is 0.05, ζ _T is 0.1, ζ _D is 0.15, m _w0 is 1.27 × 10 ⁻² kg / s, and the steam flow S1 in the introduction portion 1 0.10MPa pressure _{P s} of, when a 0.13MPa or 0.15 MPa,, was calculated change in the discharge pressure _{P D} at the time of changing the internal diameter _{D T} of the throat portion 3. Here, 1 atmosphere is 0.1024 MPa. The throat portion 3 has a circular cross section. At this time, π (D _T / 2) ² = A ₁ holds for the internal cross-sectional area A ₁ .

Figure 25 is a diagram showing the relationship between the inner diameter D _T and the discharge pressure P _D of the throat portion 3. FIG. 26 is a diagram showing first-order differential coefficients of the curve shown in FIG. FIG. 27 is a diagram showing second-order differential coefficients of the curve shown in FIG. When deriving FIGS. 25 to 27, calculation was performed by changing the value of _DT in steps of 0.01 mm. As shown in FIG. 25, for the value of any of the pressure _{P s,} also to reduce the inner diameter _{D T} of 6.0 mm, the discharge pressure _{P D} was substantially constant. However, for the value of any of the pressure _{P s,} the inner diameter _{D T} of about 1.0mm as the critical value, the critical value less than the inner diameter _{D T} is (for example 600 .mu.m) in the discharge pressure _{P D} is nonlinearly rapidly increased It was confirmed from the analysis of the formula (1). Further, as shown in FIG. 26, first-order differential coefficient of a curve showing the relationship between the inner diameter _{D T} and the pressure _{P s} shown in FIG. 25 is almost zero when the inner diameter _{D T} is greater than 1.0 mm. However, when the critical value is about 1.0 mm and the inner diameter _DT is smaller than the critical value, it becomes smaller than 0 and then decreases rapidly. Furthermore, as shown in FIG. 27, second order derivative of the curve showing the relationship between the inner diameter _{D T} and the pressure _{P s} shown in FIG. 25 is almost zero when the inner diameter _{D T} is greater than 1.0 mm. However, when the critical value is about 1.0 mm and the inner diameter _DT is smaller than the critical value, it becomes larger than 0 and then increases rapidly.

Therefore, in the unit steam injector 10, the inner diameter D _T of the throat portion 3 or the internal cross-sectional area A _1, by discharge pressure P _D is a critical value (inner diameter or cross-sectional area) smaller than the inner diameter or cross-sectional area which _increases, It is possible to realize a high discharge pressure that could not be achieved conventionally. In such small inner diameter or cross-sectional area than the critical value, the first curve representing relative changes in the internal diameter D _T or internal cross-sectional area A ₁ of the throat portion 3, a change in the discharge pressure P _D (i.e., the curve shown in FIG. 25) The rank differential coefficient is smaller than 0. Further, the second order differential coefficient is larger than zero. Therefore, a high discharge pressure P _D is realized by setting the inner diameter D _T or the inner sectional area A ₁ where the differential coefficient of the first or second floor changes from 0.

In the above FIG. 25, 26 and 27, when the inner diameter D _T is greater than the critical value, the discharge pressure P _D is substantially constant, the first floor and second floor of the derivative of the curve showing the change almost 0. Therefore, the critical value can be defined as a value at which the first- or second-order differential coefficient changes from zero. On the other hand, when the inner diameter D _T is greater than the critical value, rather than the discharge pressure P _D is substantially constant, even if the first-order and second-order differential coefficient of the curve showing the change is not zero. In such a case, a value at which the second-order differential coefficient increases by 10% or more in accordance with a decrease in the inner diameter D _T or the inner cross-sectional area A ₁ may be defined as a critical value. For example, when the inner diameter _DT is decreased from 1.0 mm to 0.9 mm and the second-order differential coefficient is increased by 10% from 1.0 to 1.1, the critical value of the inner diameter _DT is 1 It may be defined as 0.0 mm.

The critical value of the discharge pressure P _D is increased (inner diameter or cross-sectional area) is changed by the value of each parameter included in the formula (1). Therefore, in consideration of the value of each parameter, by setting the inner diameter D _T or internal cross-sectional area A ₁ of the throat portion 3 to be less than the critical value, it is possible to obtain a high discharge pressure P _D. For example, when the refrigerant is not water but another refrigerant, the parameter relating to water may be replaced with the parameter relating to the refrigerant to be used to set the inner diameter D _T or the internal sectional area A ₁ of the throat portion 3.

Then, in the formula (1), the internal cross-sectional area _{A 1} of the throat portion 3 and 2.83 × ¹⁰ -7 ^{m 2} (600μm as the inner diameter _{D T),} the _{m w0} 1.27 × ¹⁰ -2 kg / s, 1.43 × 10 ⁻² kg / s, or 1.59 × 10 ⁻² kg / s, the discharge pressure P _D when the pressure P _s of the steam flow S1 in the introduction unit 1 is changed The change of was calculated.

Figure 28 is a diagram showing the relationship between the pressure P _s and the discharge pressure P _D of the vapor stream S1 in the introductory part 1. As shown in FIG. 28, it was confirmed from the analysis of equation (1) that it is possible to increase the discharge pressure P _D as increasing the pressure P _s.

Note that, when the inner diameter D _T or the internal cross-sectional area A ₁ of the throat portion 3 is reduced in this way, the discharge amount of the unit steam injector 10 decreases, but a plurality of like the steam injector 100 according to the first embodiment. By integrating the unit vapor injectors 10, it is possible to increase the discharge amount while realizing a small size and high discharge pressure.

Next, a steam injector was actually fabricated using a resin material, and an experiment was performed to verify its operation. FIG. 29 is a diagram schematically showing the configuration of the manufactured unit vapor injector (sample 1). In Sample 1, a drain pipe 5 and a check valve 6 were provided as shown in FIG. The A _s0 / A _w0 of Sample 1 was 36.2. In addition, six types of samples were prepared. That is, it has the same configuration as sample 1 except that no check valve is provided (sample 2), and has the same configuration as sample 1 except that the check valve and drain pipe are not provided (sample 3). 27, with A _s0 / A _{w0 set} to 7.2 (sample 4), the same configuration as sample 1 except that no check valve is provided (sample 5), check The sample is the same as sample 1 except that no valve and drain pipe are provided (sample 6). Further, the configuration shown in FIG. 29 is further provided with a mechanism capable of making A _s0 / A _w0 variable (sample 7). Such a variable mechanism is realizable by comprising so that the protrusion amount to the mixing part 2 of the liquid flow introduction part 1a can be changed.

In addition, as a common structure of the samples 1-7, the length of the mixing part 2 is 22.5 mm, the inner diameter of the mixing part 2 opposite to the throat part 3 is 3.4 mm, and the liquid flow W1 is introduced. the cross-sectional area _{a w0} 1.94 M ² and (as the internal diameter 1.57 mm), and 600μm an inner diameter _{D T} of the throat portion 3, of the diffuser portion 4 in length and 14.4 mm, the discharge portion 4a of the diffuser portion 4 The inner diameter was 2.0 mm. The drain tube 5 has an inner diameter of 0.45 mm.

Also in this experiment, water was used as a refrigerant, and an experimental system capable of adjusting the experimental conditions as follows was used. First, the pressure P _s of the vapor flow in the introduction part can be adjusted in the range of 0.11 MPa to 0.15 MPa. In addition, the temperature T _w0 of the liquid flow can be adjusted in the range of 11.9 ° C. to 26 ° C., and the temperature T _{s0 of the} vapor flow can be adjusted in the range of 101.4 ° C. to 111.2 ° C. Moreover, the flow velocity m _w0 of the liquid flow in the introduction part can be adjusted in the range of 1.59 ml / s to 2.20 ml / s (note that the density of the liquid flow is, for example, 958 kg / m ³ ). Further, the dissolved oxygen amount DO _w or DO _s of the liquid flow or the vapor flow to be introduced can be adjusted in the range of 0.8 mg / l to 8.0 mg / l.

(Experiment 1)
Using the steam injector of sample 3 (A _s0 / A _w0 = 36.2, without drain pipe and check valve), when a liquid flow of T _w0 = 12.6 ° C was first introduced, mixing in the steam injector The water liquid statically accumulated in the throat and throat. Next, a steam flow of P _s = 0.11 MPa and T _s0 = 102.3 ° C. was introduced in this state. Then, the flow of the liquid occurred in the mixing part, the refrigerant flow was discharged from the discharge part of the diffuser part, and the operation of the steam injector was confirmed.

(Experiment 2)
Using the steam injector of sample 4 (A _s0 / A _w0 = 7.2, with drain pipe and check valve), first, T _w0 = 24.5 ° C., m _w0 = 1.59 ml / s, DO _w = A liquid flow of 1.64 mg / l was introduced and then a vapor flow was introduced. Then, the flow of the liquid occurs in the mixing unit, the refrigerant flow is discharged from the discharge unit of the diffuser unit, and the operation of the steam injector is confirmed, but the operation may become unstable.

FIG. 30 is a diagram showing the pressure of the steam flow introduced and the pressure in the drain pipe during the stable operation and the unstable operation. The horizontal axis is the elapsed time from the start of measurement. In FIG. 30, P _in indicates the pressure _in the drain pipe, and P _s indicates the pressure of the vapor flow. “Stable” means that the steam injector is in a stable operation state, and “Unstable” means that the steam injector is in an unstable operation state.

As shown in FIG. 30, at the time of stable operation P _in is less than P _s, the mixing portion had become negative pressure. On the other hand, during unstable operation lower than P _s is P _in, mixing portion has a positive pressure, and is unstable the values of P _s, that the introduction of a stable vapor stream is in a state not performed Was confirmed.

(Experiment 3-1, 3-2, 3-3)
Using the steam injector of sample 7 (A _s0 / A _w0 variable, with drain pipe and check valve), first, T _w0 = 21.7 ° C., m _w0 = 1.91 ml / s, DO _w = 2.4 mg / L liquid flow was introduced, and then an experiment was conducted in which a vapor flow of P _s = 0.13 MPa and DO _s = 3.5 mg / l was introduced. Note that A _s0 / A _w0 was set to 4.4, 15.1, or 38.3.

Then, the steam injector does not operate in the case of A _s0 / A _w0 = 4.4 and A _s0 / A _w0 = 38.3, and in the case of A _s0 / A _w0 = 15.1, from the discharge unit of the diffuser unit A refrigerant flow with a high discharge pressure was discharged, and the operation of the steam injector was confirmed.

As a result of further experiments by the present inventors, the value of A _s0 / A _w0 is preferably in the range of 7 to 30 in terms of the operation of the steam injector, and is stable operation in the case of 10 to 20 inclusive. Even more preferable.

  In the above-described embodiment, the structure of the unit injector and the refrigerant flow junction is formed by joining two plate-shaped constituent members. For example, two or more plate-shaped or non-plate-shaped members are formed. The shape of each constituent member may be designed so that the configuration of the unit injector and the refrigerant flow junction is formed by joining the constituent members.

  In the above embodiment, the steam injector is formed by joining a set of constituent members, but the present invention is not limited to this, and may be formed by other methods.

  In the above-described embodiment, the plurality of unit steam injectors may have the same size (internal cross-sectional area, length, angle) of the mixing unit, the throat unit, and the diffuser unit among the plurality of unit steam injectors. However, different ones may be included. In the configuration in which the unit steam injectors have the same size, the discharge amount can be increased and the discharge pressure can be increased under certain operating conditions. On the other hand, in a configuration that includes unit steam injectors of different sizes, if the size is designed so that the optimum operating conditions of each unit steam injector deviate from each other, even if the operating conditions change, the operating conditions An operating unit steam injector can be included. As a result, it is possible to realize a steam injector that operates under a wide range of operating conditions.

  Further, the present invention is not limited by the above embodiment. What was comprised combining each component mentioned above suitably is also contained in this invention. Further effects and modifications can be easily derived by those skilled in the art. Therefore, the broader aspect of the present invention is not limited to the above-described embodiment, and various modifications can be made.

DESCRIPTION OF SYMBOLS 1, 1 'introduction part 1a Liquid flow introduction part 1b Steam flow introduction part 2 Mixing part 3 Throat part 4 Diffuser part 4a Discharge part 5 Drain pipe 6 Check valve 10 Unit steam injector 20 Compressor 30 Condenser 40 Evaporator 50 Air Liquid separator 100 Vapor injector 101, 102, 103, 104, 105 Plate-shaped components 101a, 102a Refrigerant liquid supply port 101b, 102b Refrigerant vapor discharge port 102c, 105a Refrigerant liquid discharge port 102d, 105b Refrigerant vapor supply port 102e Refrigerant liquid Flow path 102f Refrigerant vapor flow path 102g Refrigerant flow merge flow path 106 Refrigerant flow outlet 1000, 2000 Heat pump device C1, C2 region F1 Refrigerant flow H1, H2 Heat P Electric power S1 Vapor flow W1 Liquid flow

Claims (20)

An introduction part for introducing a liquid flow of the refrigerant and a vapor flow of the refrigerant;
A mixing section that has a shape in which an internal cross-sectional area decreases toward the traveling direction of the liquid flow, and mixes the liquid flow in the form of a jet and the vapor flow to form a refrigerant flow;
A throat section formed on the output side of the mixing section;
A diffuser portion that discharges the refrigerant flow from the discharge portion with an increased internal cross-sectional area from the throat portion toward the traveling direction of the refrigerant flow;
A plurality of unit steam injectors with
A liquid flow path and a vapor flow path for supplying each of the liquid flow and the vapor flow of the refrigerant to each introduction portion of each unit vapor injector;
A steam injector comprising:
The steam injector is formed by joining a set of components,
Each of the set of component members is formed with a groove or a hole having a shape obtained by dividing the introduction part, the mixing part, the throat part, and the diffuser part into a plurality of parts, and the introduction part, the mixing part The throat portion and the diffuser portion are formed by the groove or the hole when the pair of constituent members are joined . The set of component members is plate-shaped and joined together in a stacked state,
At least 2 or more, the steam injector according to claim 1, characterized in that arranged along the main surface of the plate-like component of the plurality of unit steam injector. 3. The steam injector according to claim 2 , wherein a flow path that communicates each of the introduction portions of the unit steam injectors arranged along the main surface of the plate-like component is formed. The set of component members is plate-shaped and joined together in a stacked state,
The steam injector according to any one of claims 1 to 3 , wherein at least two or more of the plurality of unit steam injectors are arranged along a stacking direction of the plate-like constituent members. 5. The steam injector according to claim 4 , wherein a flow path that communicates each of the introduction portions of the unit steam injectors arranged along the stacking direction of the plate-like constituent members is formed. The set of component members are joined together in a stacked state,
The steam injector according to claim 1 , wherein the plurality of unit steam injectors extend along a stacking direction of the constituent members. Steam injector according to any one of claims 1-6, wherein the set of components is characterized in that it is joined by diffusion bonding. In the unit steam injector, when the internal cross-sectional area of the throat portion decreases the internal cross-sectional area of the throat portion, the discharge pressure of the refrigerant flow discharged from the discharge portion of the diffuser portion increases nonlinearly. The steam injector according to any one of claims 1 to 7 , wherein the steam injector has a cross-sectional area smaller than a critical cross-sectional area. The internal cross-sectional area of the throat portion is an interior in which a first-order differential coefficient of a curve representing a change in the discharge pressure of the refrigerant flow with respect to a change in the internal cross-sectional area of the throat portion is less than 0 or a second-order differential coefficient is greater than 0. The steam injector according to claim 8 , which has a cross-sectional area. The internal cross-sectional area of the throat portion is A ₁ , the mass flow rate and flow velocity of the liquid flow in the introduction portion are m _w0 and u _w0 , respectively, and the mass flow rate and flow velocity of the vapor flow in the introduction portion are m _s0 and u _s0 , respectively. , Mass flow rate and flow velocity of the refrigerant flow in the throat portion are m ₁ and u ₁ , respectively, and pressure loss coefficients in the mixing portion, the throat portion, and the diffuser portion are ζ _N , ζ _T , ζ _D , and the liquid flow, respectively. density [rho _{w of,} when the discharge pressure in the discharge portion of the refrigerant flow to P _D, the steam injector according to claim 8 or 9, characterized in that the following equation holds (1).

The steam injector according to any one of claims 8 to 10 , wherein an inner section of the throat portion is circular, and a diameter of the inner section is 2 mm or less. The steam injector according to claim 11 , wherein a diameter of the internal cross section is 1 mm or less. In the mixing section, the cross-sectional area A _W of a region where the liquid stream is _introduced, the cross-sectional area of a region where the vapor stream is introduced when the A _S, A _{s0 /} A _w0 is a 7 to 30 The steam injector according to any one of claims 8 to 12 , characterized in that: The steam injector according to claim 13 , wherein the A _s0 / A _w0 is 10 or more and 20 or less. The steam injector according to any one of claims 1 to 14 , further comprising a drain pipe formed to communicate with the outside air from the inside of the mixing unit. The steam injector according to claim 15 , wherein the drain pipe is provided with a check valve. The introduction unit includes a liquid flow inlet portion, and the steam flow introduction portion of claim 1-16, characterized in that it comprises a heat-insulating layer interposed between the liquid flow inlet portion and the vapor flow introduction portion The steam injector as described in any one. The steam injector according to any one of claims 1 to 17 , wherein the refrigerant is water or alternative chlorofluorocarbon. An introduction part for introducing a liquid flow of the refrigerant and a vapor flow of the refrigerant;
A mixing section that has a shape in which an internal cross-sectional area decreases toward the traveling direction of the liquid flow, and mixes the liquid flow in the form of a jet and the vapor flow to form a refrigerant flow;
A throat section formed on the output side of the mixing section;
A diffuser portion that discharges the refrigerant flow from the discharge portion with an increased internal cross-sectional area from the throat portion toward the traveling direction of the refrigerant flow;
A plurality of unit steam injectors with
A liquid flow path and a vapor flow path for supplying each of the liquid flow and the vapor flow of the refrigerant to each introduction portion of each unit vapor injector;
With
In the unit steam injector, when the internal cross-sectional area of the throat portion decreases the internal cross-sectional area of the throat portion, the discharge pressure of the refrigerant flow discharged from the discharge portion of the diffuser portion increases nonlinearly. A steam injector having a cross-sectional area smaller than a critical cross-sectional area. A compressor for compressing the refrigerant;
A condenser for condensing the refrigerant;
An evaporator for evaporating the refrigerant;
The steam injector according to any one of claims 1 to 19, wherein the refrigerant flow and the liquid flow of the refrigerant are introduced, and the refrigerant flow whose pressure is increased is discharged from a discharge portion of the diffuser portion. ,
A heat pump device comprising:

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