JP2014218937A - Steam injector and heat pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a steam injector at a higher discharge pressure and a heat pump device using the same.SOLUTION: A steam injector comprises: an introduction part introducing a liquid flow of refrigerant and a steam flow of the refrigerant; a mixture part having a shape in which an internal cross-sectional area is reduced toward a forward direction of the liquid flow, mixing up the liquid flow in a jet state and the steam flow inside, and forming a refrigerant flow; a throat part formed on an output side of the mixture part; and a diffuser part having a shape in which an internal cross-sectional area is reduced from the throat part toward a forward direction of the refrigerant flow. The internal cross-sectional area of the throat part is smaller than a critical cross-sectional area in a case in which a discharge pressure of the refrigerant flow discharged from a discharge portion of the diffuser part linearly increases when the internal cross-sectional area of the throat part is reduced.

Description

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

  A refrigeration cycle using an ejector is 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

  By the way, in consideration of application to a heat pump apparatus such as the above-described refrigeration cycle, a steam injector having a higher discharge pressure is required in order to improve energy efficiency represented by COP or the like.

  This invention is made | formed in view of the above, Comprising: It aims at providing the steam injector with higher discharge pressure, and a heat pump apparatus 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 diffuser portion that has a shape in which an internal cross-sectional area expands from the throat portion toward a traveling direction of the refrigerant flow, and discharges the refrigerant flow with increased pressure from a discharge portion, and includes an interior of the throat portion. The cross-sectional area is smaller than the critical cross-sectional area where the discharge pressure of the refrigerant flow discharged from the discharge portion of the diffuser portion increases nonlinearly when the internal cross-sectional area of the throat portion is decreased. Features.

  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.

In the steam injector according to the present invention, in the above invention, in the mixing unit, when the cross-sectional area of the region where the liquid flow is introduced is A _W0 and the cross-sectional area of the region where the vapor flow is introduced is A _s0 , 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.

  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 a 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, The steam injector according to the invention described above, which discharges a refrigerant flow whose pressure is increased from a discharge part of the diffuser part.

  According to the present invention, it is possible to realize a steam injector having a higher discharge pressure and a heat pump device using the same.

FIG. 1 is a schematic configuration diagram of a steam injector according to the first embodiment. FIG. 2 is an enlarged view of a main part of the introduction part and the mixing part of FIG. FIG. 3 is a diagram for explaining an operational characteristic prediction model of a steam injector. FIG. 4 is a diagram illustrating the relationship between the inner diameter of the throat portion and the discharge pressure. FIG. 5 is a diagram showing first-order differential coefficients of the curve shown in FIG. FIG. 6 is a diagram illustrating the second derivative of the curve shown in FIG. FIG. 7 is a diagram illustrating the relationship between the pressure of the steam flow and the discharge pressure in the introduction section. FIG. 8 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. FIG. 9 is a block diagram of the heat pump device according to the second embodiment. FIG. 10 is a block diagram of the heat pump device according to the third embodiment.

  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 dimensions and ratios of elements are different from actual ones. Moreover, the part from which the relationship and ratio of a mutual dimension differ also in between drawings is contained.

  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. It was discovered for the first time and arrived at the present invention.

(Embodiment 1)
FIG. 1 is a schematic configuration diagram of a steam injector according to the first embodiment. As shown in FIG. 1, the steam injector 10 includes an introduction part 1, a mixing part 2, a throat part 3, a diffuser part 4, a drain pipe 5, and a check valve 6. Hereinafter, the configuration and operation of the steam injector 10 will be described.

  The introduction unit 1 includes a nozzle-like liquid flow introduction unit 1a that introduces the refrigerant liquid flow W1, and a vapor flow introduction unit 1b that is formed on both sides of the liquid flow introduction unit 1a and introduces the refrigerant vapor flow S1. Have. 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.

  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 lower side of the sheet of FIG. In the first embodiment, the mixing unit 2 has a circular cross section, but may have another shape such as a rectangular 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.

FIG. 2 is an enlarged view of a main part of the introduction unit 1 and the mixing unit 2 of FIG. As shown in FIG. 2, the vapor flow S1 introduced from the vapor flow introduction portion 1b joins and mixes with the liquid flow W1 from the outer peripheral side of the jet-like liquid flow W1 introduced from the liquid flow introduction portion 1a. . In addition, the code | symbol C1 has shown the area | region which introduce | transduces the liquid flow W1 and mixes with the vapor flow S1 in the mixing part 2. FIG. 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 .}

  Returning to FIG. 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 circular cross section, but may have another shape such as a rectangular 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 circular cross section, but may have another shape such as a rectangular 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 drain pipe 5 is formed so as to communicate from the inside of the mixing unit 2 to the outside. The drain pipe 5 is provided with a check valve 6. The drain pipe 5 has a function of exhausting excess steam in the mixing unit 2. By exhausting excess steam in this way, the operation stability of the steam injector 10 is enhanced. During the operation of the steam injector 10, a negative pressure is generated inside the mixing unit 2 as described above. The check valve 6 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 steam injector 10.

  The steam injector 10 includes, for example, an introduction unit 1, a mixing unit 2, a throat unit 3, a diffuser unit 4, and a drain pipe in each of a set of two or more structural members (for example, plate-shaped structural members). A groove or hole having a shape obtained by dividing 5 into a plurality of parts may be formed, and a set of constituent members formed with the groove or hole may be joined. At this time, each of the introduction portion 1, the mixing portion 2, the throat portion 3, the diffuser portion 4, and the drain pipe 5 is formed by combining grooves or holes formed in the respective constituent members when a set of constituent members are joined. Formed by. The constituent material of the constituent member may be, for example, a resin material, but the constituent member is made of metal or the like, and the pair of constituent members are joined by diffusion joining or the like, so that the discharge pressure of the refrigerant flow F1 is high. Sufficient bonding strength that can withstand it can be obtained. As a metal material which comprises a structural member, what has high heat insulation, such as stainless steel material, is preferable.

  Here, in the steam injector 10 according to the first embodiment, the internal cross-sectional area of the throat portion 3 is set smaller than a predetermined critical cross-sectional area. Thereby, the discharge pressure of the refrigerant flow discharged from the discharge part 4a of the diffuser part 4 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. 3 is a diagram for explaining an operational characteristic prediction model of a steam injector. In FIG. 3, the symbol “0” indicates the start point of the region where the liquid flow W1 and the vapor flow S1 are mixed (see the regions C1 and C2 in FIG. 2). 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, the flow speeds m ₁ , u ₁ , the mixing part 2, the throat part 3, and the pressure loss coefficients 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} when the inner diameter _{D T} of the throat portion 3 is varied from 6.0mm to 300μm . 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 4 is a diagram showing the relationship between the inner diameter D _T and the discharge pressure P _D of the throat portion 3. FIG. 5 is a diagram showing first-order differential coefficients of the curve shown in FIG. FIG. 6 is a diagram illustrating the second derivative of the curve shown in FIG. When deriving FIGS. 4 to 6, the calculation was performed by changing the value of _DT in steps of 0.01 mm. As shown in FIG. 4, 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. 5, first-order differential coefficient of a curve showing the relationship between the inner diameter D _T and the pressure P _s shown in FIG. 4 is substantially 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. 6, second order derivative of the curve showing the relationship between the inner diameter D _T and the pressure P _s shown in FIG. 4 is substantially 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, the steam injector 10 according to the first embodiment, the inner diameter D _T of the throat portion 3 or the internal cross-sectional area A _1,, threshold discharge pressure P _D is increased (inner diameter or cross-sectional area) smaller than the inner diameter or cross-sectional By setting the area, a high discharge pressure, which could not be achieved conventionally, is realized. 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. 4) 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 4, 5 and 6, 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, to obtain a high discharge pressure P _D as the effect of the present invention Can do. 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 7 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. 7, 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.

Next, a steam injector was actually fabricated using a resin material, and an experiment was performed to verify its operation. There are seven types of produced steam injectors. That is, the configuration of the first embodiment shown in FIG. 1, with A _s0 / A _{w0 set} to 36.2 (sample 1), and the same configuration as sample 1 except that no check valve is provided (sample) 2) The sample has the same configuration as sample 1 (sample 3) except that the check valve and drain pipe are not provided. Also, the configuration of the first embodiment shown in FIG. 1 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) The same configuration as that of sample 1 (sample 6) except that the check valve and the drain pipe are not provided. Further, the configuration of the first embodiment shown in FIG. 1 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} and 1.94 M ² (as the inner diameter of 1.57 mm), and an inner diameter _{D T} of the throat portion 3 and 600 .mu.m, the diffuser section 4 a 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. 8 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. 8, P _in denotes the pressure in the drain pipe, P _s represents the pressure of the steam 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. 8, 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.

(Embodiment 2)
FIG. 9 is a block diagram of a heat pump apparatus according to Embodiment 2 of the present invention. As shown in FIG. 9, the heat pump apparatus 100 includes a steam injector 10 according to the first embodiment, a compressor 20, a condenser 30, an evaporator 40, and a 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 100 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 steam injector 10 introduces the refrigerant vapor flow supplied from the evaporator 40 and the refrigerant liquid flow supplied from the condenser 30, and converts the refrigerant flow whose pressure is increased into the discharge unit 4 a ( (See FIG. 1). 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 device 100, energy lost as a vortex in the expansion valve in the heat pump device using the expansion valve can be recovered by the steam injector 10. Further, in this heat pump device 100, the burden on the compressor 20 is reduced by the steam injector 10, so that 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 100 functions as a high-efficiency heat pump device with improved COP. The heat pump device 100 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. 10 is a block diagram of a heat pump apparatus according to Embodiment 3 of the present invention. As shown in FIG. 10, the heat pump device 200 includes a steam injector 10 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 200, the vapor injector 10 introduces the refrigerant vapor flow supplied from the compressor 20 and the refrigerant liquid flow supplied from the gas-liquid separator 50 with the pressure increased by the pump P. Then, the refrigerant flow whose pressure has been increased is discharged from the discharge part 4a (see FIG. 1) of the diffuser part 4. The condenser 30 is supplied with the refrigerant flow whose pressure is increased from the vapor injector 10, dissipates the heat as heat H <b> 1, 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 P. 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 200, the vapor injector 10 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. As a result, the heat pump device 200 functions as a high-efficiency heat pump device with improved COP. The heat pump device 200 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.

  The present invention is not limited to 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 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 Steam injector 20 Compressor 30 Condenser 40 Evaporator 50 Gas-liquid separator 60 Expansion valve 70 Pump 100, 200 Heat pump device C1, C2 region F1 Refrigerant flow H1, H2 Heat P Electric power S1 Steam flow W1 Liquid flow

Claims (11)

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;
With
The internal cross-sectional area of the throat portion is smaller than the critical cross-sectional area where the discharge pressure of the refrigerant flow discharged from the discharge portion of the diffuser portion increases nonlinearly when the internal cross-sectional area of the throat portion is decreased. A steam injector characterized by its 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 1, 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 1 or 2, characterized in that the following equation holds (1).

  The steam injector according to any one of claims 1 to 3, 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 4, wherein a diameter of the inner cross section is 1 mm or less. In the mixing unit, A _s0 / A _w0 is 7 or more and 30 or less, where A _W0 is a cross-sectional area of the region where the liquid flow is introduced and A _s0 is a cross-sectional area of the region where the vapor flow is introduced. The steam injector according to any one of claims 1 to 5. The steam injector according to claim 6, 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 7, 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 8, wherein the drain pipe is provided with a check valve.   The steam injector according to any one of claims 1 to 9, wherein the refrigerant is water or alternative chlorofluorocarbon. A compressor for compressing the refrigerant;
A condenser for condensing the refrigerant;
An evaporator for evaporating the refrigerant;
The vapor injector according to any one of claims 1 to 10, wherein the refrigerant flow and the liquid flow of the refrigerant are introduced, and the refrigerant flow having an increased pressure is discharged from a discharge portion of the diffuser portion. ,
A heat pump device comprising:

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