Patent Application
20180080482
This application is based on and incorporates herein by reference Japanese Patent Application No. 2015-045871 filed on Mar. 9, 2015.
The present disclosure relates to an ejector that draws a fluid by a drawing effect of a jetted fluid jetted at high velocity, and an ejector-type refrigeration cycle that includes the ejector.
Conventionally, Patent Document 1 discloses an ejector that draws a refrigerant through a refrigerant suction port by a drawing effect of a jetted refrigerant jetted at high velocity, the jetted refrigerant and the drawn refrigerant being mixed, a pressure of the mixed refrigerant being increased in the ejector. Patent Document 1 discloses an ejector-type refrigeration cycle that is a vapor-compression-type refrigeration cycle device including the ejector as a refrigerant decompression device.
In the ejector of Patent Document 1, a passage forming member having a circular cone shape is provided in a body, and a refrigerant passage is defined between the body and a circular cone-shaped side surface of the passage forming member. A cross-sectional shape of the refrigerant passage is a circular annular shape. The most upstream part of the refrigerant passage is used as a nozzle passage through which a high-pressure refrigerant is decompressed and ejected, and the most downstream part of the refrigerant passage is used as a diffuser passage in which the jetted refrigerant and the drawn refrigerant are mixed, a pressure of the mixed refrigerant being increased in the diffuser passage.
Moreover a swirl space, which is a swirl flow generation portion generating a swirl flow in the refrigerant flowing into the nozzle passage, is defined in the body of the ejector of Patent Document 1. In the swirl space, the refrigerant on a swirl center side is decompressed and boiled by being swirled the subcooled liquid-phase refrigerant about a center axis of the nozzle, and a gas-phase refrigerant (air column) having a column shape is generated on the swirl center side. The two-phase separated refrigerant on the swirl center side flows into the nozzle passage.
According to this, in the ejector of Patent Document 1, boiling of the refrigerant flowing through the nozzle passage is enhanced by using, as a boiling core, an air bubble generated on an interface between the gas-phase refrigerant and the liquid-phase refrigerant of the two-phase separated refrigerant, and an efficiency of energy conversion when converting a pressure energy to a kinetic energy in the nozzle passage is intended to be improved.
Moreover, the ejector of Patent Document 1 includes an actuation device that changes a passage cross-sectional area of a refrigerant passage defined between the body and the passage forming member by moving the passage forming member. Therefore, the ejector of Patent Document 1 is intended to be actuated adequately according to the amount of the refrigerant circulating in the cycle by changing the passage cross-sectional area of the refrigerant passage according to a change of a load of the ejector-type refrigeration cycle.
According to studies by the inventors of the present disclosure, in the ejector-type refrigeration cycle of Patent Document 1, the amount of the refrigerant circulating in the cycle may be smaller than a preferable amount even though the actuation device moves the passage forming member during a high-load operation of the cycle to enlarge the passage cross-sectional area of the refrigerant passage.
The inventors of the present disclosure has studied about the causes, and it is found that the column shape of the air column formed in the swirl space is distorted when the amount of the circulating refrigerant is changed due to the change of the load of the cycle. This is because the shapes of the swirl space and a refrigerant flow-in passage through which the refrigerant flowing into the swirl space are fixed.
In detail, since a swirling speed of the refrigerant swirling in the swirl space increases during the high-load operation in which the amount of the circulating refrigerant increases, a diameter of the air column formed in the swirl space is increased. Accordingly, during the high-load operation, an inner side area of a smallest passage cross-sectional area portion of the nozzle passage into which the gas-phase refrigerant having a low density flows is likely to be large, and an outer side area into which the liquid-phase refrigerant having a high density flows is likely to be small.
Accordingly, in the ejector of Patent Document 1, a pressure loss occurring when the refrigerant flows through the smallest passage cross-sectional area portion increases even when the actuation device enlarges the passage cross-sectional area of the smallest passage cross-sectional area portion by moving the passage forming member having a circular cone shape, and accordingly a coefficient of discharge of the nozzle passage may be likely to decrease. Consequently, in the ejector-type refrigeration cycle of Patent Document 1, the amount of the circulating refrigerant may be smaller than the preferable amount during the high-load operation.
It may be considered to limit the decrease of the coefficient of discharge during the high-load operation by enlarging a diameter of a throat portion of the nozzle defining the smallest passage cross-sectional area portion. However, in such case, a proportion of the liquid-phase refrigerant to the refrigerant flowing in the nozzle passage is increased during the low-load operation, and accordingly the boiling core may become insufficient and the refrigerant may not be boiled sufficiently.
In consideration of the above-described points, it is an objective of the present disclosure to limit a decrease of an coefficient of discharge in an ejector that generates a swirl flow in a refrigerant flowing into a nozzle.
Moreover, it is another objective of the present disclosure to provide an ejector-type refrigeration cycle that is capable of limiting the decrease of the coefficient of discharge even when a load of a cycle is changed.
An ejector according to an aspect of the present disclosure is used in a vapor-compression type refrigeration cycle device and includes: a nozzle that ejects a refrigerant; a swirl flow generation portion that generates a swirl flow about a center axis of the nozzle in the refrigerant flowing into the nozzle; a body including a refrigerant suction port through which the refrigerant is drawn from an outside by a drawing effect of the ejected refrigerant ejected from the nozzle, and a pressure increasing portion in which the ejected refrigerant and the drawn refrigerant drawn through the refrigerant suction port are mixed, a pressure of the mixed refrigerant is increased in the pressure increasing portion; a passage forming member that is inserted into a refrigerant passage defined in the nozzle; and an actuation device that moves the passage forming member. The refrigerant passage defined between an inner peripheral surface of the nozzle and an outer peripheral surface of the passage forming member is a nozzle passage decompressing the refrigerant. The nozzle passage includes: a smallest passage cross-sectional area portion at which a passage cross-sectional area is decreased the most; a convergent portion that is located upstream of the smallest passage cross-sectional area portion with respect to a refrigerant flow, the passage cross-sectional area being gradually decreased in the smallest passage cross-sectional area portion; and a divergent portion located downstream of the smallest passage cross-sectional area portion with respect to the refrigerant flow, the passage cross-sectional area is gradually increased in the divergent portion. A part of the passage forming member that changes the passage cross-sectional area at the smallest passage cross-sectional area portion during the actuation device moving the passage forming member is a tip portion. The amount of displacement of the passage forming member in a direction in which the passage forming member increases the passage cross-sectional area at the smallest passage cross-sectional area portion is a positive displacement amount. The tip portion has a shape in which an increase rate of the passage cross-sectional area at the smallest passage cross-sectional area portion is increased according to an increase of the positive displacement amount.
According to this, the passage cross-sectional area of the smallest passage cross-sectional area portion can be increased when the positive displacement amount is increased compared to a case where the passage cross-sectional area of the smallest passage cross-sectional area portion is increased in proportion to the increase of the positive displacement amount. Accordingly, the passage cross-sectional area of the smallest passage cross-sectional area portion can be enlarged sufficiently by increasing the positive displacement amount during the high-load operation in which the circulating refrigerant amount is increased.
Consequently, an increase of a pressure loss occurring when the refrigerant flowing through the nozzle passage during the high-load operation can be limited, and a large decrease of a coefficient of discharge during the high-load operation can be limited even in the ejector that generates the swirl flow in the refrigerant flowing into the nozzle.
Moreover, in the ejector having the above-described features, it is preferable that an increase rate of the passage cross-sectional area of the smallest passage cross-sectional area portion increases according to an increase of the amount of the refrigerant flowing through the nozzle passage. According to this, the passage cross-sectional area of the smallest passage cross-sectional area portion during the high-load operation can be easily increased to be equal or above the passage cross-sectional area required to limit the decrease of the coefficient of discharge.
Moreover, in the ejector having the above-described features, a specific shape of the tip portion may be a shape of a solid of revolution in which a sectional area taken in a direction perpendicular to an axial direction gradually increases toward a downstream side of the refrigerant flow. Moreover, a sectional shape of a cross-section including a center axis of the tip portion may be a shape in which an increase rate of a distance from the center line to the tip portion is decreased from a tip of the tip portion.
According to another aspect of the present embodiment, an ejector-type refrigeration cycle includes the above-described ejector, and a radiator that cools a high-pressure refrigerant discharged from a compressor compressing the refrigerant, the high-pressure refrigerant is cooled to become a subcooled liquid-phase refrigerant in the radiator. The subcooled liquid-phase refrigerant flows into the swirl flow generation portion.
According to this, the ejector-type refrigeration cycle including the ejector, which is capable of limiting the decrease of the coefficient of discharge even when the load of cycle is changed, can be provided.
Hereinafter, multiple embodiments for implementing the present invention will be described referring to drawings. In the respective embodiments, a part that corresponds to a matter described in a preceding embodiment may be assigned the same reference numeral, and redundant explanation for the part may be omitted. When only a part of a configuration is described in an embodiment, another preceding embodiment may be applied to the other parts of the configuration. The parts may be combined even if it is not explicitly described that the parts can be combined. The embodiments may be partially combined even if it is not explicitly described that the embodiments can be combined, provided there is no harm in the combination.
A first embodiment of the present disclosure will be described below referring
Moreover, in the ejector-type refrigeration cycle 10 of the present embodiment, HFC refrigerant (specifically, R134a) is used, and the ejector-type refrigeration cycle 10 constitutes a subcritical refrigeration cycle in which a refrigerant pressure on a high-pressure side does not excess a critical pressure of the refrigerant. It is needless to say that HFO refrigerant (specifically, R1234yf) may be employed as the refrigerant. Moreover, a refrigeration oil that supplies lubrication to a compressor 11 is mixed to the refrigerant, and a part of the refrigeration oil circulates in the cycle together with the refrigerant.
In the ejector-type refrigeration cycle 10, the compressor 11 draws the refrigerant, increases a pressure of the refrigerant such that the refrigerant becomes a high-pressure refrigerant, and discharges the high-pressure refrigerant. Specifically, the compressor 11 of the present embodiment is an electric compressor that accommodates a fixed-capacity-type compression device and an electric motor driving the compression device in one housing.
A variety of compression devices such as a scroll-type compression device or a bane-type compression device can be used as the compression device. An actuation (a rotation speed) of the electric motor is controlled by a control signal outputted from an air conditioning control unit 50, and either an alternating-current motor or a direct-current motor can be used as the electric motor.
A refrigerant inlet side of a condensing portion 12a of a radiator 12 is connected to a discharge port of the compressor 11. The radiator 12 is a heat dissipation heat exchanger that dissipates heat from the high-pressure refrigerant to cool the high-pressure refrigerant by performing a heat exchange between the high-pressure refrigerant discharged from the compressor 11 and a vehicle outside air (outside air) blown by a cooling fan 12d.
More specifically, the radiator 12 is a so-called subcooling-type condenser including the condensing portion 12a, a receiver portion 12b, and a subcooling portion 12c. The condensing portion 12a dissipates the heat from the high-pressure gas-phase refrigerant to condense the high-pressure gas-phase refrigerant by performing the heat exchange between the high-pressure gas-phase refrigerant and the outside air blown by the cooling fan 12d. The receiver portion 12b separates the refrigerant flowing out of the condensing portion 12a into the gas-phase refrigerant and the liquid-phase refrigerant and accumulates a surplus liquid-phase refrigerant. The subcooling portion 12c performs heat exchange between the liquid-phase refrigerant flowing out of the receiver portion 12b and the outside air blown by the cooling fan 12d to subcool the liquid-phase refrigerant.
The cooling fan 12d is an electric blower whose rotation speed (the amount of blowing air) is controlled by a control voltage outputted from the air conditioning control unit 50.
A refrigerant flow inlet 21a of the ejector 20 is connected to a refrigerant outlet of the subcooling portion 12c of the radiator 12. The ejector 20 works as a refrigerant decompression device that decompresses the high-pressure liquid-phase refrigerant in a subcooled state flowing out of the radiator 12 and ejects the refrigerant to a downstream side, and the ejector 20 works as a refrigerant circulation device (refrigerant sending device) that draws (send) the refrigerant flowing out of an evaporator by a drawing effect of a jetted refrigerant jetted at a high velocity and circulates the refrigerant.
A specific configuration of the ejector 20 will be described referring to
In the nozzle 21, the needle valve 23 that has a needle shape and works as a passage forming member is provided. The refrigerant passage defined between an inner peripheral surface of the nozzle 21 and an outer peripheral surface of the needle valve 23 defines at least a part of the nozzle passage 20a that decompresses the refrigerant. Accordingly, in an area where the nozzle 21 and the needle valve 23 overlap when viewed in a direction perpendicular to an axial direction of the nozzle 21, a cross-sectional shape of the nozzle passage 20a taken along the direction perpendicular to the axial direction is an annular shape.
On an inner wall surface of the nozzle 21, a throat portion 21b defining a smallest passage cross-sectional area portion 20b in which a sectional area of the refrigerant passage decreases the most is provided. Therefore, the nozzle passage 20a includes a convergent portion 20c on a refrigerant upstream side of the smallest passage cross-sectional area portion 20b, and a divergent portion 20d on a refrigerant downstream side of the smallest passage cross-sectional area portion 20b. In the convergent portion 20c, the sectional area of the refrigerant passage is gradually decreased toward the smallest passage cross-sectional area portion 20b. In the divergent portion 20d, the sectional area of the refrigerant passage is gradually enlarged.
In other words, the sectional area of the refrigerant passage in the nozzle passage 20a of the present embodiment changes similarly to a laval nozzle. Moreover, in the present embodiment, the refrigerant passage cross-sectional area of the nozzle passage 20a is changed such that the ejection refrigerant jetted from a refrigerant ejection port 21c is equal to or more than the sound speed during a normal operation of the ejector-type refrigeration cycle 10.
Furthermore, a cylinder portion 21d extending coaxially with an axis line of the nozzle 21 is provided upstream of a part defining the nozzle passage 20a of the nozzle 21. A swirl space 20e that swirls the refrigerant flowing into the nozzle 21 is provided inside the cylinder portion 21d. The swirl space 20e has an approximately circular column shape extending coaxially with the axis line of the nozzle 21.
Moreover, a refrigerant inflow passage, through which the refrigerant flows from an outside of the ejector 20 into the swirl space 20e, extends in a tangential direction of an inner wall surface of the swirl space 20e when viewed from a direction of an center axis of the swirl space 20e. According to this, the subcooled liquid-phase refrigerant flowing out of the radiator 12 and into the swirl space 20e flows along the inner wall surface of the swirl space 20e and swirls about the center axis of the swirl space 20e.
Since a centrifugal force is exerted on the refrigerant swirling in the swirl space 20e, a pressure of the refrigerant on a center axis side is lower than a pressure of the refrigerant on an outer peripheral side in the swirl space 20e. In the present embodiment, dimensions of the swirl space 20e, for example, are set such that the refrigerant pressure on the center line side in the swirl space 20e is decreased to a pressure of a saturated liquid-phase refrigerant or a pressure at which the refrigerant is boiled due to a pressure decrease (a cavitation occurs) during a low-load operation, in which a thermal load of the ejector-type refrigeration cycle 10 is relatively low, and a middle-load operation, in which the thermal load of the ejector-type refrigeration cycle 10 is a medium value.
Such adjustment of the refrigerant pressure on the center line side in the swirl space 20e can be achieved by adjusting a swirling speed of the refrigerant swirling in the swirl space 20e. Moreover, the adjustment of the swirling speed can be achieved by, for example, adjusting a dimensional relationship such as a ratio of the passage cross-sectional area of the refrigerant inflow passage to a sectional area of the swirl space 20e taken along a line perpendicular to the axial direction. In the present embodiment, the swirling speed means a flow rate of the refrigerant around an outermost part of the swirl space 20e in the swirl direction.
Accordingly, in the present embodiment, the cylinder portion 21d and the swirl space 20e constitutes a swirl flow generating portion that swirls, around the axis of the nozzle 21, the subcooled liquid-phase refrigerant flowing into the nozzle 21. That is, in the present embodiment, the ejector 20 (specifically, nozzle 21) and the swirl flow generating portion are provided integrally with each other.
The body 22 is formed of metal (for example, aluminum) or resin shaped in an approximately circular cylinder shape, and the body 22 works as a fixation member that supports and fixes the nozzle 21 in an inside thereof and constitutes an outer body of the ejector 20. Specifically, the nozzle 21 is housed and fixed by press-fitting to one end of the body 22 in a longitudinal direction. Accordingly, the refrigerant is prevented from leaking through a fixation portion (press-fitting portion) of the nozzle 21 and the body 22.
A refrigerant suction port 22a extending through the body 22 is provided in a part of an outer peripheral surface of the body 22 which corresponds to an outer peripheral side of the nozzle 21. The refrigerant suction port 22a is communicated with the refrigerant ejection port 21c of the nozzle 21. The refrigerant suction port 22a is a through-hole through which the refrigerant flowing out of the evaporator 14 is drawn from the outside to the inside due to a drawing effect of the ejection refrigerant jetted from the nozzle 21.
A suction passage 20f and a diffuser portion 20g are provided in the body 22. The suction passage 20f guides the refrigerant drawn through the refrigerant suction port 22a to the refrigerant ejection port side of the nozzle 21. The diffuser portion 20g is a pressure increasing portion in which the refrigerant drawn through the refrigerant suction port 22a into the inside of the ejector 20 is mixed with the ejected refrigerant, a pressure of the mixed refrigerant being increased in the diffuser portion 20g.
The diffuser portion 20g is defined as a space that is positioned so as to continue to an outlet of the suction passage 20f. The refrigerant passage area is gradually enlarged in the space. According to this, the diffuser portion 20g performs a function for mixing the ejected refrigerant and the drawn refrigerant, decreasing the flow rate of the mixed refrigerant, and increasing the pressure of the mixed refrigerant of the ejected refrigerant and the drawn refrigerant. In other words, the diffuser portion 20g performs a function for converting a velocity energy of the mixed refrigerant to a pressure energy.
The needle valve 23 works as a passage forming member and changes the passage cross-sectional area of the nozzle passage 20a. Specifically, the needle valve 23 is made of resin and has a needle shape tapered from the diffuser portion 20g side toward the refrigerant upstream side (nozzle passage 20a side). The needle valve 23 may be made of metal.
Moreover, the needle valve 23 is located coaxially with the nozzle 21. An electric actuator 23a including a stepper motor as a driving device that moves the needle valve 23 in the axial direction of the nozzle 21 is connected to an end portion of the needle valve 23 on the diffuser portion 20g side. The actuation of the electric actuator 23a is controlled by a control pulse outputted from the air conditioning control unit 50.
In contrast, a tip portion 23b of the needle valve 23 that defines the smallest passage cross-sectional area portion 20b on the inner peripheral side of the throat portion 21b of the nozzle 21 is provided in an end portion of the needle valve 23 on the nozzle passage 20a side. That is, the tip portion 23b changes the passage cross-sectional area (smallest passage cross-sectional area) at the smallest passage cross-sectional area portion 20b when the needle valve 23 is moved in the axial direction.
The tip portion 23b has a shape of a solid of revolution in which the sectional area taken in the direction perpendicular to the axial direction gradually increases toward the downstream side of the refrigerant flow. The shape of the solid of revolution is a 3D shape that is formed when a 2D shape is rotated about a line (center line) that lies on the same plane as the 2D shape. A tip of the tip portion 23b has a hemisphere shape. Accordingly, in a sectional surface including the center line of the tip portion 23b, an outline of the tip of the tip portion 23b is a parabola.
Therefore, a tip of the sectional shape of the tip portion 23b indicated by a solid line in
According to this, the tip portion 23b of the ejector 20 of the present embodiment has a shape in which an increase rate (a gradient of a thick and solid line of
The positive displacement amount δ is a displace amount of the needle valve 23 when the needle valve 23 is moved toward a direction in which the passage cross-sectional area of the smallest passage cross-sectional area portion 20b is increased. Accordingly, when the needle valve 23 is in contact with the nozzle 21 to close the nozzle passage 20a, the positive displacement amount δ is zero.
According to the ejector 20 of the present embodiment, when the positive displacement amount δ is increased, the passage cross-sectional area of the smallest passage cross-sectional area portion 20b can be enlarged more compared to a case where the passage cross-sectional area of the smallest passage cross-sectional area portion 20b is increased in proportion to the increase of the positive displacement amount δ indicated by a dashed line of
In the ejector 20 of the present embodiment, since the tip portion 23b is employed, the increase rate (a gradient of thick and solid line of
In the ejector 20 of the present embodiment, the passage cross-sectional area of the smallest passage cross-sectional area portion 20b is enlarged more compared to a case where the passage cross-sectional area of the smallest passage cross-sectional area portion 20b is increased in proportion to the increase of the nozzle flow rate Gnoz as indicated by a dashed line of
An inlet side of a gas-liquid separator 13 is connected to a refrigerant outlet of the diffuser portion 20g of the ejector 20 as shown in
A gas-phase refrigerant outlet of the gas-liquid separator 13 is connected to an inlet side of the compressor 11. In contrast, the liquid-phase refrigerant outlet of the gas-liquid separator 13 is connected to a refrigerant inlet side of the evaporator 14 through a fixed throttle 13a that is a decompression device. As the fixed throttle 13a, an orifice or a capillary tube can be employed, for example.
The evaporator 14 is a heat absorbing heat exchanger that causes the low-pressure refrigerant to evaporate and to perform heat absorbing effect by performing a heat exchange between the low-pressure refrigerant flowing therein and the blown air that is blown from the a blowing fan 14a toward the vehicle compartment. The blowing fan 14a is an electric blower whose rotation speed (an amount of the blown air) is controlled by a control voltage outputted from the air conditioning control unit 50. A refrigerant outlet of the evaporator 14 is connected to a refrigerant suction port 22a side of the ejector 20.
Next, a general configuration of an electric controller of the present embodiment will be described. The air conditioning control unit 50 is constituted by a microcomputer including CPU, ROM and RAM, for example, and its peripheral circuit. The air conditioning control unit 50 performs calculations and processing based on control programs stored in the ROM to control actuations of the above-described electric actuators 11, 12d, 14a, 23a, for example.
The air conditioning control unit 50 is connected to sensors for air conditioning control such as an inside air temperature sensor for detecting a vehicle interior temperature (interior temperature) Tr, an outside air temperature sensor for detecting the temperature of an outside air Tam, an insolation sensor for detecting the amount of insolation As in the vehicle compartment, an evaporator outlet side temperature sensor (evaporator outlet side temperature detection device) 51 for detecting the temperature Te of the refrigerant on the outlet side of the evaporator 14 (evaporator outlet side temperature), an evaporator outlet side pressure sensor (evaporator outlet side pressure detection device) 52 for detecting the pressure Pe of the refrigerant on the outlet side of the evaporator 14, a radiator outlet side temperature sensor for detecting the temperature Td of the refrigerant on the outlet side of the radiator 12, and an outlet side pressure sensor for detecting a pressure Pd on the outlet side of the radiator 12, and detection values of the sensors are inputted to the air conditioning control unit 50.
Moreover, an input side of the air conditioning control unit 50 is connected to an operation panel, which is not shown, located close to an instrument panel in a front part of the vehicle compartment, and an operation signal of an operation switch provided in the operation panel is inputted to the air conditioning control unit 50. The operation switch provided in the operation panel includes an air conditioning actuation switch for requiring the air conditioning of the vehicle compartment, and a vehicle compartment temperature setting switch for setting a vehicle inside temperature Tset.
In the air conditioning control unit 50, control units that control actuations of various control target devices connected to the output side of the control unit are integrated with each other, and a part of the air conditioning control unit 50 (hardware and software) controlling respective control target device constitutes a control unit for respective control target device.
For example, in the present embodiment, a part controlling the actuation of the compressor 11 constitutes a discharge capacity control portion 50a, and a part controlling the actuation of electric actuator 23a constitutes a valve opening degree control portion 50b. It is needless to say that the discharge capacity control portion 50a and the valve opening degree control portion 50b may be provided as separate control units from the air conditioning control unit 50.
Next, actuations of the above-described configurations of the present embodiment will be described. In the vehicular air conditioning device of the present embodiment, when the air conditioning actuation switch of the operation panel is turned on (ON), the air conditioning control unit 50 executes an air conditioning control program that is preliminary stored.
In the air conditioning control program, the detection signals of the above-described sensors for air conditioning control and operation signals of the operation panel are read. A target blown air temperature TAO that is a target temperature of the air blown into the vehicle compartment is calculated based on the detection signals and the operation signals.
The target blown air temperature TAO is calculated based on an expression F1 below.
TAO=Kset×Tset−Kr×Tr−Kam×Tam−Ks×As+C (F1)
Tset is the vehicle inside temperature that is set by the temperature setting switch, Tr is the inside temperature detected by the inside temperature sensor, Tam is the outside temperature detected by the outside temperature sensor, and As is the amount of the insolation detected by the insolation sensor. Kset, Kr, Kam, and Ks are control gains, and C is a constant for correction.
Moreover, in the air conditioning control program, operation states of the control target devices connected to the output side of the air conditioning control unit 50 are decided based on the calculated target blown air temperature TAO and the detection signals of the sensors.
For example, the refrigerant discharge capacity of the compressor 11, i.e. the control signal outputted to the electric motor of the compressor 11, is decided as described below. First, a control map that is preliminary stored in a memory circuit is referred based on the target blown air temperature TAO, and then a target evaporator air temperature TEO of the blown air blown from the evaporator 14 is decided.
The control signal outputted to the electric motor of the compressor 11 is decided based on a deviation (TEO−Te) between the evaporator outlet side temperature Te detected by the evaporator outlet side temperature sensor 51 and the target evaporator air temperature TEO such that the evaporator outlet side temperature Te becomes close to the target evaporator air temperature TEO by using a feedback control method.
Specifically, the discharge capacity control portion 50a of the present embodiment controls the refrigerant discharge capacity (rotation speed) of the compressor 11 such that the amount of the refrigerant circulating in the cycle increases according to increase of the deviation (TEO−Te), i.e. increase of the thermal load of the ejector-type refrigeration cycle 10.
The control pulse outputted to the electric actuator 23a that moves the needle valve 23 is decided such that the degree of superheat SH of the refrigerant on the outlet side of the evaporator 14, which is calculated based on the evaporator outlet side temperature Te and the evaporator outlet side pressure Pe detected by the evaporator outlet side pressure sensor 52, comes closer to a predetermined reference superheat degree KSH.
Specifically, the valve opening degree control portion 50b of the present embodiment controls the actuation of the electric actuator 23a such that the passage cross-sectional area of the smallest passage cross-sectional area portion 20b is increased according to the increase of the degree of superheat SH of the refrigerant on the outlet side of the evaporator 14. Therefore, in the ejector 20 of the present embodiment, thermal load of the ejector-type refrigeration cycle 10 becomes higher, and the passage cross-sectional area of the smallest passage cross-sectional area portion 20b is increased according to the increase of the nozzle flow rate Gnoz.
The air conditioning control unit 50 outputs the decided control signals to corresponding control target devices. Subsequently, a control routine is repeated until a stop of the actuation of the vehicular air conditioning device is required, in which the above-described detection signals and operation signals are read, the target blown air temperature TAO is calculated, the actuation states of the control target devices are decided, and the control signals are outputted.
Therefore, in the ejector-type refrigeration cycle 10, the refrigerant flows as indicated by the thick and solid arrow of
In more detail, the high-temperature and high-pressure refrigerant (point a of
A pressure of the subcooled liquid-phase refrigerant flowing out of the subcooling portion 12c of the radiator 12 is isentropically reduced in the nozzle passage 20a of the ejector 20 and ejected (from the point b to a point c of
The refrigerant flowing out of the evaporator 14 (point h of
The suction passage 20f of the present embodiment is formed such that the passage cross-sectional area is gradually decreased in the refrigerant flow direction. Therefore, the pressure of the drawn refrigerant that passes the suction passage 20f decreases (from the point h to the point h′ of
In the diffuser portion 20g, a kinetic energy of the refrigerant is converted into a pressure energy by an increase of the refrigerant passage cross-sectional area. Accordingly, a pressure of the mixed refrigerant is increased while the ejected refrigerant and the drawn refrigerant are mixed (from a point e to the point d of
The liquid-phase refrigerant separated in the gas-liquid separator 13 is decompressed by the fixed throttle 13a (from a point g′ to the point g of
The ejector-type refrigeration cycle 10 of the present embodiment is actuated as described above and is capable of cooling the blown air blown to the vehicle compartment.
In the ejector-type refrigeration cycle 10 of the present embodiment, the refrigerant whose pressure is increased in the diffuser portion 20g of the ejector 20 is drawn into the compressor 11. Accordingly, the ejector-type refrigeration cycle 10 is capable of reducing power consumption of the compressor 11 to improve the coefficient of performance (COP) of the cycle compared to a conventional refrigeration cycle device in which a refrigerant evaporation pressure in an evaporator and a pressure of the refrigerant drawn to a compressor are almost the same.
Since the ejector 20 of the present embodiment includes the needle valve 23 that is the passage forming member and the electric actuator 23a that is a driving device, the passage cross-sectional area of the smallest passage cross-sectional area portion 20b can be adjusted according to a change of the load of the ejector-type refrigeration cycle 10. Accordingly, the ejector 20 can be properly actuated according to the change of the load of the ejector-type refrigeration cycle 10.
Moreover, according to the ejector 20 of the present embodiment, since the refrigerant is swirled in the swirl space 20e during the low-load operation and the middle-load operation of the ejector-type refrigeration cycle 10, the pressure of the refrigerant on a center side of the swirl in the swirl space 20e can be reduced such that the refrigerant becomes to be the saturated liquid-phase refrigerant or is to be boiled due to the pressure decrease (a cavitation occurs).
According to this, since the gas-phase refrigerant having a column shape (air column) is provided on an inner side of a center axis of the swirl as shown in
Since the refrigerant in the two-phase-separated state in the swirl space 20e flows into the nozzle passage 20a, boiling of the refrigerant is enhanced by a wall surface boiling, which occurs when the refrigerant is separated from the outer peripheral wall surface of the refrigerant passage having a circular annular shape, and an interface boiling, which is caused by a boiling core generated by the cavitation of the refrigerant on the center axis side of the refrigerant passage having a circular annular shape.
According to this, the refrigerant flowing into the smallest passage cross-sectional area portion 20b of the nozzle passage 20a becomes a gas-liquid mixed state in which the gas-phase refrigerant and the liquid-phase refrigerant are uniformly mixed. The flow of the refrigerant in the gas-liquid mixed state is throttled (choking) around the smallest passage cross-sectional area portion 20b, and the refrigerant in the gas-liquid mixed state achieving sound speed due to the choking is accelerated in and jetted from the divergent portion 20d.
In the low-load operation and the middle-load operation of the cycle, since the refrigerant in the gas-liquid mixed state is efficiently accelerated up to sound speed by boiling enhancement due to both the wall surface boiling and the interface boiling, the efficiency of the energy conversion in the nozzle passage 20a can be improved.
In the ejector 20 of the present embodiment, shapes of the swirl space 20e and a flow-in refrigerant passage through which the refrigerant flowing into the swirl space 20e may have the same shapes. Accordingly, when the amount of the circulating refrigerant flow is changed due to the change of the load of the cycle, the shape of the air column formed in the swirl space 20e is also changed.
In more detail, since the velocity of the swirling flow of the refrigerant swirling in the swirl space 20e increases during a high-load operation of the cycle, a diameter φ of the air column formed in the swirl space 20e is larger than that during a the low-load operation and the middle-load operation. Therefore, during the high-load operation, the inner side area in the smallest passage cross-sectional area into which a low density gas-phase refrigerant flows is likely to be large, and the outer side area into which a high density liquid-phase refrigerant flows is likely to be small.
Accordingly, during the high-load operation, the pressure loss occurring when the refrigerant flows through the smallest passage cross-sectional area portion 20b is likely to increase even when the electric actuator 23a moves the needle valve 23 such that the passage cross-sectional area of the smallest passage cross-sectional area portion 20b increases, and accordingly coefficient of discharge of the nozzle passage 20a may decrease.
In contrast, in the ejector 20 of the present embodiment, the increase rate of the passage cross-sectional area of the smallest passage cross-sectional area portion 20b is increased according to the increase of the positive displacement amount δ of the needle valve 23. Accordingly, the passage cross-sectional area of the smallest passage cross-sectional area portion 20b can be sufficiently increased such that the coefficient of discharge does not decrease by increasing the positive displacement amount δ during the high-load operation of the ejector-type refrigeration cycle 10.
Specifically, the passage cross-sectional area of the smallest passage cross-sectional area portion 20b can be increased compared to a case where a needle valve whose tip portion is circular cone shape as indicated by thin and dashed line of
Consequently, according to ejector 20 of the present embodiment, increase of the pressure loss occurring when the refrigerant flowing through the nozzle passage 20a during the high-load operation can be limited, and a large decrease of coefficient of discharge during the high-load operation can be limited.
Moreover, in the ejector 20 of the present embodiment, the increase rate of the passage cross-sectional area of the smallest passage cross-sectional area portion 20b becomes large according to increase of the nozzle flow rate Gnoz as described with reference to
In a common nozzle through which the refrigerant that does not swirl about an axis, when a pressure difference between an inlet side fluid pressure and an outlet side fluid pressure of the nozzle is constant, the nozzle flow rate Gnoz can be increased in proportion to an increase of the passage cross-sectional area of the smallest passage cross-sectional area portion.
Therefore, when the increase rate of the passage cross-sectional area of the smallest passage cross-sectional area portion 20b becomes large according to increase of the nozzle flow rate Gnoz, the passage cross-sectional area of the smallest passage cross-sectional area portion 20b during the high-load operation can be surely over the passage cross-sectional area required for flowing the nozzle flow rate Gnoz. Accordingly, the passage cross-sectional area of the smallest passage cross-sectional area portion 20b during the high-load operation is easily increased over the passage cross-sectional area required for limiting the decrease of efficient of discharge.
Moreover, in the ejector 20 of the present embodiment, the tip portion 23b has the shape of a solid of revolution in which the sectional area taken in the direction perpendicular to the axial direction gradually increases, and the tip portion 23b has a shape in which an increase rate of a distance from the center line to the tip portion 23b is decreased from the tip. Accordingly, the tip portion 23b of the needle valve 23, by which the increase rate of the passage cross-sectional area of the smallest passage cross-sectional area portion 20b is increased according to increase of the positive displacement amount δ, can be easily obtained.
In the present embodiment, as compared with the first embodiment, an example of an ejector-type refrigeration cycle 10a will be described below, in which an ejector 25 is employed as shown in the overall configuration diagram of
The ejector 25 of the present embodiment is a device in which configurations corresponding to the ejector 20, the gas-liquid separator 13, and the fixed throttle 13a described in the first embodiment are integrated (modularized) with each other. Accordingly, the ejector 25 may be referred to as “an ejector with gas-liquid separation function” or “an ejector module”.
Specific configuration of the ejector 25 will be described below referring to
The ejector 25 includes a body 30 that is formed by combining multiple components as shown in
The housing body 31 includes: a refrigerant inlet 31a into which the refrigerant flowing out of a radiator 12 flows; a refrigerant suction port 31b through which the refrigerant flowing out of an evaporator 14 is drawn; a liquid-phase refrigerant outlet 31c through which the liquid-phase refrigerant separated in a gas-liquid separation space 30f defined in the body 30 flows out toward a refrigerant inlet side of the evaporator 14; and a gas-phase refrigerant outlet 31d through which the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out toward an inlet side of a compressor 11, for example.
Moreover, in the present embodiment, an orifice 31i that is a decompression device decompressing the refrigerant flowing into the evaporator 14 is provided in a liquid-phase refrigerant passage through which the gas-liquid separation space 30f is communicated with the liquid-phase refrigerant outlet 31c. The gas-liquid separation space 30f of the present embodiment corresponds to the gas-liquid separator 13 described in the first embodiment, and the orifice 31i of the present embodiment corresponds to the fixed throttle 13a described in the first embodiment.
The nozzle 32 of the present embodiment is formed of a metal material (e.g. stainless alloy) having an approximately circular cone shape tapered in the refrigerant flow direction. The nozzle 32 is fixed to the inside of the housing body 31 by press-fitting, for example, such that an axial direction is a vertical direction (up-down direction of
A refrigerant inlet passage 31e that provides a connection between the refrigerant inlet 31a and the swirl space 30a extends in a tangential direction of an inner wall surface of the swirl space 30a when viewed from a direction of an center axis of the swirl space 30a. According to this, the refrigerant flowing into the swirl space 30a through the refrigerant inlet passage 31e flows along the inner wall surface of the swirl space 30a and swirls about the center axis of the swirl space 30a. Accordingly, in the present embodiment, a part of the body defining the swirl space 30a and the swirl space 30a constitute a swirl flow generation portion.
Moreover, in the present embodiment, dimensions of the swirl space 30a are set such that a refrigerant pressure on the center line side in the swirl space 30a is decreased to a pressure of a saturated liquid-phase refrigerant or a pressure at which the refrigerant is boiled due to a pressure decrease (a cavitation occurs) during a low-load operation, in which a thermal load of the ejector-type refrigeration cycle 10a is relatively low, and a middle-load operation, in which the thermal load of the ejector-type refrigeration cycle 10a is a medium value.
A decompression space 30b, which decompresses the refrigerant flowing out of the swirl space 30a and flows the refrigerant to a downstream side, is defined in the nozzle 32. The decompression space 30b has a shape of a solid of revolution in which a circular column space and a conical frustum space continuing from a lower side of the circular column space and gradually diverging in the refrigerant flow direction are joined with each other. A center axis of the decompression space 30b is coaxial with the center axis of the swirl space 30a.
A passage forming member 35 is provided in the decompression space 30b. The passage forming member 35 performs the same function of the needle valve 23 described in the first embodiment. Specifically, the passage forming member 35 is made of resin and has a circular cone shape whose sectional area is increased according to a distance from the decompression space 30b. A center axis of the passage forming member 35 is coaxial with the center axis of the decompression space 30b.
According to this, at least a part of a nozzle passage 25a, whose cross-section is a circular annular shape, for decompressing the refrigerant is defined between an inner peripheral surface of a part of the nozzle 32 defining the decompression space 30b and an outer peripheral surface of the passage forming member 35, as shown in
Moreover, a throat portion 32a defining a smallest passage cross-sectional area portion 25b, in which the refrigerant passage cross-sectional area is decreased the most, is provided on an inner wall surface of the nozzle 32. Therefore, the nozzle passage 25a includes a convergent portion 25c on a refrigerant upstream side of the smallest passage cross-sectional area portion 25b, and a divergent portion 25d on a refrigerant downstream side of the smallest passage cross-sectional area portion 25b. In the convergent portion 25c, the sectional area of the refrigerant passage is gradually decreased toward the smallest passage cross-sectional area portion 25b. In the divergent portion 25d, the sectional area of the refrigerant passage is gradually enlarged.
Accordingly, the refrigerant passage cross-sectional area of the nozzle passage 25a of the present embodiment also changes similarly to a laval nozzle. Moreover, in the present embodiment, the refrigerant passage cross-sectional area of the nozzle passage 25a is changed such that an ejected refrigerant jetted from the nozzle passage 25a is equal to or more than the sound speed during a normal operation of the ejector-type refrigeration cycle 10a.
Moreover, a tip portion 35a that defines the smallest passage cross-sectional area portion 25b on an inner side of the throat portion 32a of the nozzle 32 is provided on a tip side of the passage forming member 35 of the present embodiment, as shown in
The tip portion 35a has a shape in which an increase rate of the passage cross-sectional area of the smallest passage cross-sectional area portion 20b increases according to an increase of a positive displacement amount δ, similarly to the tip portion 23b of the needle valve 23 of the first embodiment. Accordingly, in the ejector 25 of the present embodiment, the passage cross-sectional area of the smallest passage cross-sectional area portion 25b can be increased more than a case where the passage cross-sectional area of the smallest passage cross-sectional area portion 20b is increased in proportion to the increase of the positive displacement amount δ, similarly to the first embodiment.
Dashed lines of
Next, the middle body 33 shown in
A flow-in space 30c in which the refrigerant flowing through the refrigerant suction port 31b is accumulated is defined between an upper surface of the middle body 33 and an inner wall surface of the housing body 31. Moreover, an suction passage 30d through which the flow-in space 30c and a refrigerant downstream side of the decompression space 30b are communicated with each other is defined between an inner peripheral surface of the through-hole of the middle body 33 and an outer peripheral surface of a lower part of the nozzle 32.
A pressure increasing space 30e that has an approximately conical frustum shape gradually enlarged in the refrigerant flow direction is provided on a refrigerant downstream side of the through-hole of the suction passage 30d of the middle body 33. The pressure increasing space 30e is a space in which the ejected refrigerant jetted from the above-described nozzle passage 25a and the drawn refrigerant drawn through the suction passage 30d are mixed. A center axis of the pressure increasing space 30e is coaxial with the center axes of the swirl space 30a and the decompression space 30b.
A lower part of the passage forming member 35 is positioned in the pressure increasing space 30e. A refrigerant passage defined between an inner peripheral surface of a part of the middle body 33 defining the pressure increasing space 30e and a lower part of an outer peripheral surface of the passage forming member 35 has a shape whose sectional area is gradually increased toward the refrigerant downstream side. According to this, the refrigerant passage is capable of converting the velocity energy of the mixed refrigerant of the ejected refrigerant and the drawn refrigerant into the pressure energy.
Accordingly, the refrigerant passage defined between the inner peripheral surface of the middle body 33 defining the pressure increasing space 30e and the lower part of the outer peripheral surface of the passage forming member 35 constitutes a diffuser passage that works as a diffuser (pressure increasing portion) in which the ejected refrigerant and the drawn refrigerant are mixed and the pressure of the mixed refrigerant is increased.
Next, the actuation mechanism 37 located inside the middle body 33 will be described. The actuation mechanism 37 includes a diaphragm 37a that is a pressure moved member having a circular thin plate shape. Specifically, the diaphragm 37a is fixed by welding, for example, so as to partition a circular column space defined on the outer peripheral side of the middle body 33 into an upper space and a lower space, as shown in
The upper (flow-in space 30c side) space of the two spaces partitioned by the diaphragm 37a constitutes an enclosure space 37b in which a thermostatic medium whose pressure changes according to a temperature of the refrigerant on the outlet side of the evaporator 14 (the refrigerant flowing out of the evaporator 14). The thermostatic medium whose primary component is the refrigerant circulating in the ejector-type refrigeration cycle 10a is enclosed in the enclosure space 37b so as to have a predetermined density.
In contrast, the lower space of the two spaces partitioned by the diaphragm 37a constitutes an introduction space 37c into which the refrigerant on the outlet side of the evaporator 14 is introduced through a communication passage that is not shown. Accordingly, the temperature of the refrigerant on the outlet side of the evaporator 14 is transferred to the thermostatic medium enclosed in the enclosure space 37c through the diaphragm 37a and a lid member 37d that separates the flow-in space 30c from the enclosure space 37b.
Moreover, the diaphragm 37a changes its shape according to a difference between an internal pressure of the enclosure space 37b and a pressure of the refrigerant on the outlet side of the evaporator 14 flowing into the introduction space 37c. Therefore, the diaphragm 37a is preferred to be made of a material that has high elasticity, high thermal conductivity, and high strength. Specifically, a thin metal plate made of stainless (SUS 304) or EPDM (ethylene propylene diene monomer rubber) including a ground fabric may be used as the diaphragm.
At a center part of the diaphragm 37a, one end side end portion (upper side end portion) of an actuation bar 37e having a circular column shape is bonded. The actuation bar 37e transfers an actuation force from the actuation mechanism 37 to the passage forming member 35 to move the passage forming member 35. The other end side end portion (lower side end portion) of the actuation bar 37e is located to be in contact with an outer peripheral side of a bottom surface of the passage forming member 35.
As shown in
Specifically, when the temperature (degree of superheat) of the refrigerant on the outlet side of the evaporator 14 increases, a saturation pressure of the thermostatic medium enclosed in the enclosure space 37b increases, and accordingly the difference between the internal pressure of the enclosure space 37b and the pressure of the introduction space 37c becomes large. According to this, the diaphragm 37a is moved toward the introduction space 37c side, and the pressure exerted on the passage forming member 35 by the actuation bar 37e increases. Therefore, when the temperature of the refrigerant on the outlet side of the evaporator 14 increases, the passage forming member 35 moves in a direction (downward in the vertical direction) in which the passage cross-sectional area at the smallest passage cross-sectional area portion 25b increases.
In contrast, when the temperature (degree of superheat) of the refrigerant on the outlet side of the evaporator 14 decreases, the saturation pressure of the thermostatic medium enclosed in the enclosure space 37b decreases, and accordingly the difference between the internal pressure of the enclosure space 37b and the pressure of the introduction space 37c decreases. According to this, the diaphragm 37a moves toward the enclosure space 37b side, and the stress exerted on the passage forming member 35 by the actuation bar 37e decreases. Therefore, when the temperature of the refrigerant on the outlet side of the evaporator 14 decreases, the passage forming member 35 moves in a direction (upward in the vertical direction) in which the passage cross-sectional area of the smallest passage cross-sectional area portion 25b decreases.
In the actuation mechanism 37 of the present embodiment, since the diaphragm 37a moves the passage forming member 35 according to the degree of superheat of the refrigerant on the outlet side of the evaporator 14, the passage cross-sectional area at the smallest passage cross-sectional area portion 25b is adjusted such that a degree of superheat of the refrigerant on the outlet side of the evaporator 14 comes close to a predetermined reference superheat degree KSH. The reference superheat degree KSH can be changed by adjusting the stress exerted by the coil spring 40.
A gap between the actuation bar 37e and the middle body 33 is sealed by a seal member such as O-ring that is not shown, and accordingly the refrigerant does not leak through the gap even when the actuation bar 37e moves.
In the present embodiment, multiple (three in the present embodiment) spaces having circular column shape are formed in the middle body 33, and the diaphragm 37a having the circular thin plate shape is fixed in each of the spaces to constitute multiple actuation mechanisms 37. Moreover, multiple actuation mechanisms 37 are arranged with regular intervals about the center axis so as to uniformly transfer the actuation force to the passage forming member 35.
Next, the lower body 34 is formed of a metal material having a circular column shape and fixed in the housing body 31 by screwing, for example, so as to close a bottom surface of the housing body 31. The gas-liquid separation space 30f that separates the refrigerant flowing out of the diffuser passage defined in the pressure increasing space 30e is defined between an upper side of the lower body 34 and the middle body 33.
The gas-liquid separation space 30f has a shape of solid of revolution that is approximately circular column shape, and the center axis of the gas-liquid separation space 30f is coaxial with the center axes of the swirl space 30a, the decompression space 30b, and the pressure increasing space 30e, for example. In the gas-liquid separation space 30f, the refrigerant is separated into the gas-phase refrigerant and the liquid-phase refrigerant by a centrifugal force generated when the refrigerant swirls about the center axis. Moreover, a capacity of the gas-liquid separation space 30f is set such that a surplus refrigerant cannot be accumulated substantially even when the amount of the refrigerant circulating in the cycle varies due to a change of load of the cycle.
At a center part of the lower body 34, a pipe 34a extending toward the upper side and having a circular cylinder shape is provided coaxially with the gas-liquid separation space 30f. The liquid-phase refrigerant separated in the gas-liquid separation space 30f is temporarily accumulated on an outer peripheral side of the pipe 34a and flows through the liquid-phase refrigerant outlet 31c. In the pipe 34a, a gas-phase refrigerant outlet passage 34b through which the gas-phase refrigerant separated in the gas-liquid separation space 30f is guided to the gas-phase refrigerant outlet 31d of the housing body 31 is provided.
The above-described coil spring 40 is fixed on an upper end portion of the pipe 34a. The coil spring 40 works as a vibration absorbing member that reduces a vibration of the passage forming member 35 due to a pulse of the pressure generated when the refrigerant is decompressed. Moreover, an oil return hole 34c through which a refrigeration oil is returned to the compressor 11 through the gas-phase refrigerant outlet passage 34b is formed in the bottom surface of the gas-liquid separation space 30f.
Accordingly, the ejector 25 of the present embodiment includes: the swirl space 30a generating a swirl flow in the refrigerant flowing through the refrigerant inlet 31a; the decompression space 30b decompressing the refrigerant flowing out of the swirl space 30a; the passage for drawing the refrigerant (flow-in space 30c, suction passage 30d) communicating with the refrigerant downstream side of the decompression space 30b to flow the refrigerant drawn from outside; and the body 30 including the pressure increasing space 30e in which the ejected refrigerant jetted from the decompression space 30b and the drawn refrigerant drawn through the passage for drawing 30c, 30d are mixed. The ejector 25 includes: the passage forming member 35 at least a part of which is located in the decompression space 30b and the pressure increasing space 30e, the passage forming member 35 having a circular cone shape in which the cross-sectional area increases from the decompression space 30b; and the actuation device 37 that outputs a driving force moving the passage forming member 35. The refrigerant passage defined between the inner peripheral surface of a part of the body 30 defining the decompression space 30b and the outer peripheral surface of the passage forming member 35 is the nozzle passage 25a that works as a nozzle from which the refrigerant flowing through the refrigerant inlet 31a is decompressed and jetted. The refrigerant passage defined between the inner peripheral surface of the body 30 defining the pressure increasing space 30e and the outer peripheral surface of the passage forming member 35 is the diffuser passage that works as the pressure increasing portion in which the ejected refrigerant and the drawn refrigerant are mixed, the pressure of the mixed refrigerant is increased in the diffuser passage. The nozzle passage 25a includes: the smallest passage cross-sectional area portion 25b at which the passage cross-sectional area is at the minimum; the convergent portion 25c defined on the refrigerant upstream side of the smallest passage cross-sectional area portion 25b, the passage cross-sectional area in the convergent portion 25c is gradually decreased toward the smallest passage cross-sectional area portion 25b; and the divergent portion 25d defined on the refrigerant downstream side of the smallest passage cross-sectional area portion 25b, the passage cross-sectional area in the divergent portion 25d is gradually increased.
Moreover, when the actuation device 37 moves the passage forming member 35, a part of the passage forming member 35 of the ejector 25 which changes the passage cross-sectional area of the smallest passage cross-sectional area portion 25b is the tip portion 35a. When the passage forming member 35 moves in a direction in which the passage cross-sectional area of the smallest passage cross-sectional area portion 25b is increased, the amount of displacement of the passage forming member 35 is the positive displacement amount δ. The tip portion 35a has a shape in which the increase rate of the passage cross-sectional area of the smallest passage cross-sectional area portion 25b is increased according to the increase of the positive displacement amount δ.
The other configurations of the ejector-type refrigeration cycle 10a are the same as the ejector-type refrigeration cycle 10 of the first embodiment. The ejector 25 of the present embodiment is a device in which multiple components constituting the cycle are integrated with each other. Accordingly, when the ejector-type refrigeration cycle 10a of the present embodiment is operated, it works in the same way as the ejector-type refrigeration cycle 10 of the first embodiment, and the same effects can be obtained.
Moreover, in the ejector 25 of the present embodiment, since the swirl space 30a that is a swirl flow generation portion is provided, high energy conversion efficiency can be obtained similarly to the first embodiment by swirling the refrigerant in the swirl space 30a during the low-load operation and the middle-load operation of the ejector-type refrigeration cycle 10a.
In the ejector 25 of the present embodiment, the tip portion 35a of the passage forming member 35 has a shape in which the increase rate of the passage cross-sectional area of the smallest passage cross-sectional area portion 25b increases according to the increase of the positive displacement amount δ. Accordingly, the passage cross-sectional area of the smallest passage cross-sectional area portion 20b can be increased such that coefficient of discharge does not decrease similarly to the first embodiment by increasing the positive displacement amount δ during the high-load operation of the ejector-type refrigeration cycle 10.
Consequently, also in the ejector 25 of the present embodiment, the increase of the pressure loss occurring when the refrigerant flows through the nozzle passage 20a during the high-load operation can be limited, and large decrease of coefficient of discharge during the high-load operation can be limited.
The present disclosure is not limited to the above-described embodiments, and it is to be noted that various changes and modifications will become apparent to those skilled in the art.
(1) In the above-described embodiments, examples where the tip of the tip portion 23b, 35a is shaped in a hemisphere shape are described, but the shape is not limited to these examples. For example, as shown in
When the tip portion 35a shown in
(2) The components constituting the ejector-type refrigeration cycle 10 are not limited to the above-described embodiments.
For example, in the above-described embodiments, an electric compressor is used as the compressor 11. However, an engine-driving type compressor which is driven by a rotational driving force transferred from an engine for vehicle travel through a pulley or a belt may be used as the compressor 11. Moreover, as the engine-driving type compressor, a capacity changeable compressor that is capable of changing a refrigerant discharge capacity according to a change of a required discharge amount, or a fixed capacity compressor that adjusts a refrigerant discharge amount by changing an operation rate of the compressor via intermitting an operation of an electromagnetic clutch can be employed.
In the above-described embodiments, a subcooling-type heat exchanger is used as the radiator 12, but an ordinary radiator that includes only the condensing portion 12a may be employed. Moreover, a receiver-integrated type condenser in which a liquid receiver (receiver) is integrated with the radiator may be employed. The liquid receiver separates the refrigerant that has dissipated heat in the radiator into a gas-phase refrigerant and a liquid-phase refrigerant and accumulates a surplus liquid-phase refrigerant.
Furthermore, in the above-described embodiment, it is described that R123a, R1234yf or the like can be employed as the refrigerant, but the refrigerant is not limited to this. For example, R600a, R410A, R404A, R32, R1234yfxf, R407C or the like may be employed. Moreover, a mix refrigerant in which some of these refrigerants are mixed may be employed.
(3) In the above-described embodiments, an example where the ejector-type refrigeration cycle 10 according to the present disclosure is used in the vehicular air conditioning device is described, but the usage of the ejector-type refrigeration cycle 10 is not limited to this. For example, the ejector-type refrigeration cycle 10 may be used in a stationary-type air conditioning device, a cooling temperature storage, a cooling-heating device for a vending machine or the like.
(4) In the above-described embodiments, the radiator 12 of the ejector-type refrigeration cycle 10 of the present disclosure is used as an outside heat exchanger that performs heat exchange between the refrigerant and the outside air, and the evaporator 14 is used as a usage side heat exchanger that cools the blown air. However, a heat pump cycle in which: the evaporator 14 may be used as the outside heat exchanger that absorbs heat from a heat source such as an outside air; and the radiator 12 may be used as an interior heat exchanger that heats a heating target fluid such as air or water, can be constituted.
Although the present disclosure has been described in connection with the preferred embodiments thereof, it is to be noted that various changes and modifications will become apparent to those skilled in the art. The present disclosure includes various changes and modifications within the equivalent. Moreover, other combinations and configurations, including more, less or only a single element, are also within the spirit and scope of the present disclosure.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2015-045871 | Mar 2015 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2016/001050 | 2/26/2016 | WO | 00 |
