WO2001027543A1 - Cycle frigorifique - Google Patents

Cycle frigorifique Download PDF

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Publication number
WO2001027543A1
WO2001027543A1 PCT/JP2000/006900 JP0006900W WO0127543A1 WO 2001027543 A1 WO2001027543 A1 WO 2001027543A1 JP 0006900 W JP0006900 W JP 0006900W WO 0127543 A1 WO0127543 A1 WO 0127543A1
Authority
WO
WIPO (PCT)
Prior art keywords
opening area
pressure
communication passage
valve body
valve
Prior art date
Application number
PCT/JP2000/006900
Other languages
English (en)
Japanese (ja)
Inventor
Nobuhiko Suzuki
Shunichi Furuya
Yuji Kawamura
Shunji Muta
Kenji Iijima
Sakae Hayashi
Hiroshi Kanai
Akihiko Takano
Hajime Mukawa
Original Assignee
Zexel Valeo Climate Control Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zexel Valeo Climate Control Corporation filed Critical Zexel Valeo Climate Control Corporation
Publication of WO2001027543A1 publication Critical patent/WO2001027543A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention refrigerant low critical point as the refrigerant, for example, about the carbon dioxide (C 0 2) refrigeration cycle using the available refrigerant in the supercritical region as such.
  • the pressure control valve controls the pressure on the outlet side of the radiator by a pressure control valve.
  • the pressure control valve is formed in a coolant flow path, and partitions the coolant flow path into an upstream space and a downstream space.
  • the valve body is configured to open the valve port when the displacement member is displaced.
  • the compressor at a low load pressure of the high pressure line is low subcritical region than the critical pressure while the variable capacity During operation, the refrigeration cycle will fluctuate intermittently even during steady-state operation where the compressor discharge rate and the load on the radiator and condenser are constant (environmental conditions are constant). The phenomenon has been confirmed.
  • the main causes are considered as follows. That is, regardless of the diaphragm type expansion device or the bellows type expansion device, the gas sealed in the expansion device expands or contracts according to the refrigerant temperature on the inlet side of the expansion device, and the valve expands or contracts. Since the position of the body is displaced and the position of the valve body is displaced in response to the refrigerant pressure on the inflow side of the expansion device, the charged gas is filled so that the relationship between the refrigerant temperature and the refrigerant pressure has optimal control characteristics. By enclosing, the opening of the expansion device is adjusted to the target opening according to the refrigerant temperature and the refrigerant pressure on the inflow side.
  • the discharge rate is originally low and the expansion device tries to close because the pressure in the high pressure line is relatively low. Work in the direction.
  • the opening degree of the expansion device is stable at a position where the optimum refrigerant pressure P is obtained for a certain refrigerant temperature T, the refrigerant temperature may become T If it is relatively high, the expansion device will close at low load due to the small opening.
  • Variable displacement compressors are designed so that the discharge rate is controlled according to the low pressure, so that the discharge rate is reduced if the low pressure is low, and the discharge rate is increased if the low pressure is high. Therefore, when the amount of refrigerant supplied to the low-pressure line decreases, the discharge amount of the compressor also decreases.
  • the compressor discharge decreases, the operation of reducing the specific volume of the refrigerant by condensing the radiator at low load, in which the cycle operates in the subcritical region, attempts to increase the volume by supplying the refrigerant. Therefore, the refrigerant pressure on the high pressure side does not rise for a while, and the closed state of the expansion device is maintained.
  • the compressor continues to discharge the refrigerant to the high pressure side little by little even in such a state, after a while, as the condensation in the radiator progresses, the area where the radiator actually performs the radiating action gradually decreases. Therefore, the operation of increasing the volume by the refrigerant discharged from the compressor is superior to the operation of reducing the specific volume of the refrigerant by the condensing operation of the radiator, and the high pressure gradually increases. Then, when the high pressure required for the cooling valve is reached, the expansion device opens and the high-pressure refrigerant flows at a stretch to the low-pressure side, and a sudden refrigerant flow occurs in a cycle in which the refrigerant flow has been almost stagnant until now. Flow occurs. It is considered that such a series of operations is repeated thereafter, resulting in intermittently large fluctuations in the cycle.
  • the shape of the valve body is reduced. In any case, it can be adjusted to the desired degree.
  • the movement of the valve element is controlled by the refrigerant. Since it is determined by the temperature and the refrigerant pressure, special consideration is required for adjusting the opening at low load. Nevertheless, the valve element used in the conventional non-electric expansion device has a ball valve as shown in FIGS.
  • the change of the valve opening (opening area of the communication passage) with respect to the high pressure (valve lift) is, as shown in FIG.
  • the valve opening (opening area of the communication passage) is approximately linear with respect to the lift (lift). Since the characteristic indicated by A, the change in the valve opening (opening area of the communication passage) increases as the high-pressure pressure decreases. However, the configuration shown in B is such that the higher the high pressure, the smaller the change in the valve opening (opening area of the communication passage) becomes.
  • a refrigeration cycle includes: a compressor that compresses a refrigerant to make a refrigerant in a high pressure line in a supercritical state according to operating conditions; and a radiator that cools the refrigerant compressed by the compressor.
  • a valve body that changes the opening area of the communication path; and a position of the valve body that is controlled in accordance with a refrigerant condition on the radiator side to change the opening area of the communication path.
  • the opening area fluctuation due to the pressure fluctuation of the high pressure space in the initial stage when the valve body of the expansion device is lifted is reduced, so that the movement of the valve body at low load with low flow rate and low pressure is reduced.
  • the valve can be made insensitive to fluctuation and the opening area of the communication passage may be minimized, that is, if the valve body is of a type that closes the communication passage by sitting on the valve seat, the expansion device is used. The possibility that the valve body easily seats on the valve seat and closes the communication passage can be reduced.
  • the valve body is formed in a shape having a characteristic of reducing the variation of the opening area with respect to the pressure variation of the high-pressure space as the opening area of the communication passage becomes smaller. Is also good.
  • the shape of the valve element such that the smaller the opening area of the communication passage is, the smaller the variation of the opening area in response to the pressure fluctuation of the high-pressure space is, and the communication passage has a through hole having the same diameter from the high-pressure space to the low-pressure space.
  • the valve body has a shape in which the change in the diameter per unit axial direction is continuously reduced from the base to the tip and the rate of decrease in the diameter is gradually increased.
  • the sensing element is capable of obtaining a stroke of the valve element substantially proportional to the high pressure, according to the above-described structure of the valve element, the valve element is Even if the stroke is the same, if the high pressure is low, the amount of change in the valve opening (opening area of the communication passage) with respect to the pressure change is small, and if the high pressure is high, the valve with respect to the pressure change is small.
  • the amount of change in the opening degree (opening area of the communication passage) increases, and the characteristics of the valve opening degree (opening area of the communication passage) with respect to the high-pressure pressure, as shown by the characteristic line in FIG.
  • the above-described configuration for obtaining the characteristics of the expansion device can also be realized by adjusting the shape of the communication passage (ie, the shape of the valve seat) instead of adjusting the shape of the valve body.
  • the shape of the communication passage may be formed such that the smaller the opening area of the passage is, the smaller the variation of the opening area with respect to the variation in pressure of the high-pressure space becomes.
  • the communication passage is configured so that the change in the passage cross-section per unit axial direction is continuously reduced from the high-pressure space to the low-pressure space, and the reduction rate of the passage cross-section is gradually reduced. Conceivable.
  • the communication passage is formed with a through hole having the same diameter from the high-pressure space to the low-pressure space.
  • the valve body is formed in a truncated cone shape in which the change in diameter per unit axial direction is continuously reduced at the same rate as going from the base to the tip, and from the position where the opening area of the communication passage becomes the minimum to the maximum.
  • the valve is being lifted to a certain position Then, even if the tip of the valve body is separated from the opening end of the communication passage, the shape of the valve body and the communication passage is optimized, and the diameter of the valve body is gradually reduced toward the front end.
  • the angle of the included angle between the generatrix of the second conical part and the generatrix of the first conical part is smaller than the angle of the included angle with the generatrix of the first conical part.
  • the angle of the included angle between the axis of the communication passage and the axis of the valve body is the angle between the axis of the valve body and the generatrix of the second conical portion.
  • the configuration may be such that it can abut on the transition from the road to the second conical road.
  • valve body has a first surface formed with a predetermined angle between the axis of the valve body and an axis thereof, and a first surface formed following the first surface further from the first surface and an axis of the valve body. Forming a second surface having an included angle formed at an angle smaller than the first surface, the characteristics of the expansion device, and the pressure of the high-pressure space at an early stage when the valve element is lifted. The variation of the entrance area with respect to the variation may be reduced.
  • the valve body is provided with a guide piece that is continuously inserted into the communication passage even when the valve is lifted, thereby adjusting the maximum opening area of the communication passage. May be cut in the axial direction to form a guide surface, and a guide receiving surface for receiving the guide surface may be formed in the communication passage for positioning.
  • the first surface of the valve body is connected to the end of the communication passage. Even if the position of the valve body where the opening area is minimized is determined by seating on the valve seat formed in the above, a stopper which is displaced integrally with the valve body is provided, and the opening area is minimized by the stopper.
  • the position of the valve element may be specified.
  • FIG. 1 is a diagram showing a configuration example of a refrigeration cycle according to the present invention.
  • FIG. 2 is an enlarged sectional view of an expansion device used in the refrigeration cycle shown in FIG.
  • FIG. 3 is an enlarged sectional view showing the vicinity of the valve body and the communication passage shown in FIG.
  • FIG. 4 is a characteristic diagram showing a change in a valve opening (opening area of a communication passage) with respect to a high pressure (valve lift) of the expansion device according to the present invention.
  • FIG. 5 is a sectional view showing another example of the expansion device.
  • FIG. 6 is an enlarged sectional view showing the vicinity of the valve body and the communication passage shown in FIG.
  • FIG. 7 shows yet another configuration example, and is an enlarged sectional view showing the vicinity of a valve body and a communication passage.
  • FIG. 8 shows yet another configuration example, and is an enlarged perspective view showing the vicinity of a valve body and a communication passage.
  • FIG. 9 is an enlarged sectional view showing the vicinity of the valve body and the communication passage shown in FIG.
  • FIG. 10 is a characteristic diagram showing a change in an opening area of a communication passage with respect to a valve lift of an expansion device.
  • FIG. 11 shows yet another configuration example, and is an enlarged perspective view showing the vicinity of a valve body and a communication passage.
  • FIG. 12 is an enlarged cross-sectional view showing the vicinity of the valve element and the communication passage shown in FIG. 11, in which the lifted state of the valve element is indicated by a solid line, and the state in which the valve element is seated on a valve seat is indicated by a broken line.
  • FIG. 13 is a diagram for explaining the included angle of each part of the valve body and the communication passage shown in FIG.
  • FIG. 14 shows yet another configuration example, and is an enlarged perspective view showing the vicinity of a valve body and a communication passage.
  • FIG. 15 is an enlarged cross-sectional view showing the vicinity of the valve body and the communication passage shown in FIG. 14, wherein the lifted state of the valve body is shown by a solid line, and the state where the valve body is seated on the valve seat is shown by a broken line. Show.
  • FIG. 16 is a view for explaining the included angle of each part of the valve element shown in FIG.
  • FIG. 17 shows yet another configuration example, and is an enlarged perspective view showing the vicinity of a valve body and a communication passage.
  • Fig. 18 is an enlarged sectional view showing the vicinity of the valve element and the communication passage shown in Fig. 17, and shows a state in which the valve element is lifted by a solid line, and a state in which the valve element is seated on a valve seat by a broken line. Show.
  • FIG. 19 shows yet another configuration example, and is an enlarged perspective view showing the vicinity of a valve body and a communication passage.
  • FIG. 20 is a perspective view showing only the stopper of FIG.
  • Fig. 21 is an enlarged cross-sectional view showing the vicinity of the valve element and the communication passage shown in Fig. 19, in which the lifted state of the valve element is indicated by a solid line, and the state in which the valve element is seated on a valve seat is indicated by a broken line. Show.
  • FIG. 22 is a characteristic diagram showing a change in a valve opening degree (opening area of a communication passage) of a communication passage with respect to a high pressure (valve lift) of a conventional expansion device.
  • a refrigeration cycle 1 includes a compressor 2 for compressing a refrigerant and a compressor 2 for cooling the refrigerant.
  • Heater 3 Internal heat exchanger 4 for exchanging heat between high-pressure line and low-pressure line 4, Expansion device 5 for depressurizing refrigerant 5, Evaporator 6 for evaporating and evaporating refrigerant, Evaporator 6 for evaporating refrigerant It has an accumulator 7 for liquid separation.
  • the discharge side (D) of the compressor 2 is connected to the high pressure passage 4a of the internal heat exchanger 4 via the radiator 3, and the outlet side of the high pressure passage 4a is connected to the expansion device 5,
  • a high-pressure line 8 is used as a path from the discharge side of the compressor 2 to the expansion device 5.
  • the outlet side of the expansion device 5 is connected to the evaporator 6, and the outlet side of the evaporator 6 is connected to the low-pressure passage 4 b of the internal heat exchanger 4 via the accumulator 7.
  • the outflow side of the low-pressure passage 4 b is connected to the suction side (S) of the compressor 2, and the path from the outflow side of the expansion device 5 to the compressor 2 is a low-pressure line 9.
  • a low critical point refrigerant as a refrigerant For example, carbon dioxide (C 0 2) is used and refrigerant compressed by the compressor 2, radiator 3 as a high-temperature high-pressure refrigerant
  • the heat is radiated and cooled here.
  • the internal heat exchanger 4 exchanges heat with the low-temperature refrigerant flowing out of the evaporator 6 to be further cooled and sent to the expansion device 5 without being liquefied.
  • the pressure is reduced in the expansion device 5 to become a low-temperature and low-pressure wet steam, and heat exchange with the air passing therethrough in the evaporator 6 to become gaseous, and thereafter, the high-pressure line 8 in the internal heat exchanger 4. It is heated by exchanging heat with the high-temperature refrigerant and returned to the compressor 2.
  • the expansion device 5 communicates with the high-pressure passage 4 a of the internal heat exchanger 4 in the housing 10 (communicates with the radiator side) and communicates with the high-pressure space 11 and the evaporator 6.
  • a low-pressure space 12 is defined by a partition wall 13, and a communication path 14 having a circular cross section having a predetermined diameter is formed in the partition wall 13 from the high-pressure space 11 to the low-pressure space 12.
  • the high-pressure space 11 accommodates a pressure-reducing control valve 15.
  • the valve 15 is joined to a valve element 17 seated on a valve seat 16 formed on the peripheral edge of the opening that opens into the high-pressure space 11 of the communication path 14, and is joined to the valve element 17 to form an integral body.
  • the bellows 18 is filled with a predetermined amount of sealing gas.
  • the opening pressure of the pressure-reducing control valve 15 and the movement of the valve element 17 are adjusted by changing the amount of gas and the type of gas sealed inside the bellows 18. Is responsive to the refrigerant pressure of the high-pressure space 11 divided by the refrigerant temperature. As shown in FIG. 3, the diameter of the valve element 17 changes continuously from its base to its tip.
  • the needle valve has a shape that gradually increases the rate of decrease in diameter, so that the smaller the opening area of the communication passage 14 becomes, the smaller the fluctuation of the opening area with respect to the pressure fluctuation of the high-pressure space 11 becomes. It is configured.
  • the radius of curvature is It may be a curve that changes continuously (decreases gradually) from the base to the tip.
  • the stroke amount of the valve element 17 is proportional to the refrigerant pressure in the high-pressure space 11.
  • the opening area of the communication passage 14, that is, the substantial opening area of the communication passage 14 can be exponentially increased as shown by the solid line in FIG.
  • the change in the area, that is, the change in the substantial opening area of the communication path 14 becomes smaller as the high pressure is lower, and becomes larger as the high pressure is higher.
  • the lower the high-pressure pressure the slower the fluctuation of the valve opening (opening area of the communication passage). Therefore, even in the case of using a variable capacity type in which the capacity is controlled and operating this cycle in a low load range where the cycle operates in a subcritical region where the high pressure is lower than the critical pressure, The possibility that the valve element 17 easily seats on the valve seat 16 and closes the communication passage 14 can be reduced, and therefore, the low pressure and the discharge amount of the compressor 2 can be significantly reduced. This can suppress the phenomenon that the refrigeration cycle 1 causes intermittent large fluctuations, and stabilize the cooling capacity at low load.
  • the above configuration has the characteristic that the smaller the opening area of the communication passage 14 with the shape of the valve element 17, the smaller the variation of the valve opening (opening area of the communication passage) with respect to the pressure fluctuation of the high-pressure space 11.
  • the shape of the communication passage 14, that is, the shape of the valve seat 16, may have the same characteristics.
  • FIG. 5 An example of the configuration is shown in FIG. 5, and the inflator 5 shown here has a valve body 17 that moves integrally with the bellows 18 as shown in FIG.
  • the shape of the communication passage 14 is gradually reduced as the shape of the communication passage 14 moves from the high-pressure space 11 to the low-pressure space 12.
  • the middle part of the communication path 14 where the diameter of the passage cross section is equal to the diameter of the valve element 17 is defined as a valve seat 16 on which the valve element 17 is seated.
  • the curvature radius is from the high-pressure space 11 to the low-pressure space. It may be a curve that changes continuously (increases gradually) toward 12. Since other configurations are the same as those of the above configuration example, the same portions are denoted by the same reference numerals and description thereof will be omitted. Even in such a configuration, the distance between the valve element 17 and the valve seat 16 increases exponentially as the valve element 17 moves away from the valve seat 16. As shown by the solid line in FIG.
  • the change in the opening area of the communication passage 14 with respect to the change in the refrigerant pressure of the refrigerant i.e., the change in the substantial opening area of the communication passage 14 becomes higher as the opening area of the communication passage 14 becomes smaller. It is possible to provide a characteristic that reduces fluctuations in the degree of reliability (opening area of the communication passage) with respect to fluctuations in the refrigerant pressure in the space 11.
  • FIG. 7 shows another configuration example.
  • the communication passage of the expansion device 5 shown here gradually reduces the diameter of the communication passage 14 from the high-pressure space 11 to the low-pressure space 12, and
  • the configuration example of FIG. 6 is that the reduction rate of the diameter is reduced toward the low-pressure space 12 so that the reduction rate of the cross section of the communication passage 14 is reduced toward the low-pressure space 12.
  • the valve element 17, which moves integrally with the bellows is formed in the shape of a truncated cone whose straight line is the generatrix. That is, the valve element 17 is formed in a shape in which the diameter continuously decreases at an equal rate from the base to the tip.
  • the middle portion of the communication passage 14 where the diameter of the passage cross section is equal to the tip diameter of the valve body 17 is defined as a valve seat 16 on which the valve body 17 is seated.
  • the bus / 5 of the communication passage 14 is a curve having a constant radius of curvature from the high pressure space 11 to the low pressure space 12 of the communication passage 14, the radius of curvature is from the high pressure space 11 to the low pressure space 1.
  • the curve may be a curve that changes continuously (increases gradually) toward 2. Further, since other configurations are the same as those of the above-described configuration example, the same portions are denoted by the same reference numerals and description thereof is omitted.
  • the fluctuation of the valve opening (opening area of the communication passage) can be made more gentle in a region where the high-pressure pressure is low, so that the compressor 2 has a low pressure.
  • the expansion device 5 The possibility that the valve element 17 easily seats on the valve seat 16 to close the communication passage 31 can be further reduced, and the remarkable decrease in low pressure and the discharge amount of the compressor 2 can be suppressed. As a result, fluctuations in the refrigeration cycle 1 that occur intermittently can be suppressed, and the cooling capacity at low load can be stabilized.
  • the valve element lifts from the position where the opening area of the communication passage becomes the smallest, and when the valve element lifts in the direction to increase the opening area of the communication passage, the communication with the pressure fluctuation in the high-pressure space starts. If the variation in the opening area of the passage can be reduced, the variation in the cycle can be suppressed.
  • the needle-shaped valve element shown in FIG. 7 is formed to have a predetermined diameter as shown in FIGS. 8 and 9, instead of the conventionally used ball valve. It may be used for the communication path 14.
  • the configuration shown in FIGS. 8 and 9 is such that the valve element 17 moving integrally with the bellows gradually reduces its diameter toward the tip and makes the bus bar straight.
  • the communication path 14 is separated from the end of the communication path 14 by a predetermined lift or more. In this example, when the diameter of the communication passage is about 2.0 mm, and the total lift amount of the valve body 17 is about 1.0 mm, the valve body 17 is located at the open end of the communication passage 14.
  • valve seat 17 With the valve seat 17 lifted by about 0.4 mm from being seated on the formed valve seat 16, the bottom surface of the valve element 17 coincides with the open end face of the communication passage 14, and further from the open end face. It is about 6 mm apart.
  • Other configurations are the same as those described above. Therefore, the same reference numerals are given to the same portions, and the description will be omitted.
  • the stroke amount of the valve element 17 is equal to the refrigerant pressure in the high-pressure space 11.
  • the pressure in the high pressure space is lower than the characteristic shown by the ball valve (I line shown by the broken line in FIG. 10).
  • the fluctuation of the opening area with respect to the pressure fluctuation of the high-pressure space becomes smaller.
  • the characteristic becomes as shown by the solid line (II line) in FIG. 10 which reaches the opening area corresponding to the passage cross section of the communication passage 17.
  • the horizontal axis represents the lift amount of the valve element (the opening area of the communication passage 14). Is the amount of lift from the position where is the minimum).
  • the expansion device 5 having such a valve body configuration when the expansion device 5 having such a valve body configuration is used, the fluctuation of the valve opening (opening area of the communication passage) in the region where the high pressure is low is more than that in the case where the conventional ball valve is used. Therefore, a variable capacity compressor whose capacity is controlled by the pressure of the low pressure line is used as the compressor 2 and this cycle is operated in a subcritical region where the high pressure is equal to or lower than the critical pressure. Therefore, even when operating in a low load range, the risk that the valve element 17 of the expansion device 5 easily seats on the valve seat 16 and closes the communication passage 31 can be further reduced. By suppressing a remarkable decrease and a remarkable decrease in the discharge amount of the compressor 2, fluctuations of the refrigeration cycle 1 that occur intermittently can be reduced, and the cooling capacity under a low load can be stabilized.
  • the lift amount until the degree of consideration (opening area of the communication passage) is maximized can be increased, the amount of refrigerant flowing to the low pressure side via the expansion device can be reduced accordingly. If the amount of the refrigerant passing through the expansion device 5 can be reduced, the valve opening time of the expansion device 5 can be lengthened, and the fluctuation due to hunting can be reduced as the valve opening time increases. From this point of view, it is difficult to further improve the characteristics of the opening area by improving only the valve 17, so that the shape of both the valve 17 and the communication passage 14 is optimal. Therefore, a combination of the valve body 1 and the communication passage 14 as shown in FIGS. 11 to 13 is considered.
  • the valve element 17 has a first conical portion 20 whose diameter gradually decreases toward the distal end, and is formed continuously from the first conical portion 20 on the distal end side and gradually toward the distal end.
  • the second conical portion 21 with respect to the axis of the valve element 17 and the generatrix of the second conical portion 21 are provided.
  • the angle of the included angle a is formed smaller than the angle of the included angle formed by the generatrix of the first conical portion 20 with respect to the axis of the valve element 17.
  • the communication path 14 is formed following the first conical path 22, which opens into the high-pressure space 11 and gradually decreases in diameter as the distance from the high-pressure space 11 decreases.
  • a second conical path 23 whose diameter gradually decreases toward the low-pressure space 12.
  • the second conical path 23 gradually decreases in diameter toward the low-pressure space 12. 2 cones
  • the angle d of the included angle with the bus of the path 23 is formed smaller than the angle d of the included angle with the bus of the first conical path 22 with respect to the axis of the communication path 14.
  • the transition from the second conical path 23 to the second conical path 23 is a valve seat 16 on which the transition from the first conical part 20 to the second conical part 21 of the valve element 17 is seated.
  • the relationship between hi, ⁇ , a, and 6 is defined as hi ⁇ ?>A> 5.
  • the expansion device 5 having such a valve body configuration when used, the fluctuation of the valve opening (opening area of the communication passage 14) in the initial region of the lift where the high pressure is reduced is shown in FIG. Like the valve body, it can be made dull, and the time until the opening area of the communication passage 14 becomes fully open can be lengthened, so that the capacity of the compressor 2 is controlled by the pressure of the low pressure line. Even when a variable displacement type is used and this cycle is operated in a low load region where the high pressure is operated in a subcritical region where the high pressure is equal to or lower than the critical pressure, the valve element 17 of the expansion device 5 has the valve seat 1. 6 can be further reduced, and the risk of blockage of the communication passage 3 1 can be further reduced, and the refrigeration cycle 1 Strange The cooling capacity can be stabilized at low load.
  • FIGS. 14 to 16 show another example of the structure of the valve element 17 and the communication path 14.
  • the valve element 17 has a pinch angle (an inclination with respect to the axis) formed with its axis. Angle) is formed at a predetermined angle (01) with the first surface 30 and the axis of the valve element 17 that is formed continuously from the first surface 30 on the distal end side. And a second surface 31 having an included angle (inclination angle with respect to the axis) larger than the first surface 30 at an angle (0 2).
  • a first surface 30 that is flatly cut at an inclination of 01 with respect to the axis from one point around the base end is formed on a columnar material
  • the second surface 31 cut into a flat shape at an inclination of 2 is formed following the first surface 30 from the middle to the tip of the valve element 17.
  • a guide surface 32 formed by pressing in a shape is formed.
  • the communication passage 14 has a passage cross section having substantially the same shape as a cross section cut by a plane passing through the middle of the first surface 30 of the valve element 17 and perpendicular to the axis.
  • the edge of the open end facing the first surface 30 is a valve seat 16. Therefore, the valve element 17 is seated on the valve seat 16 in the middle of the first surface 30 to close the communication path 14.
  • the communication passage 14 receives the guide surface 32 of the valve element 17, so that the guide receiving surface 33 for positioning the valve body 1 ⁇ in the communication passage 14 is aligned with the axis of the communication passage 14. It is formed along.
  • 01 is set to about 20 degrees
  • the cross-sectional area of the communication path 14 is set to be approximately the same as a hole having a diameter of about 1.5 to 3.0 mm.
  • the stroke amount of the valve element 17 is almost proportional to the refrigerant pressure of the high-pressure space 11, so that the valve element 17 separates from the valve seat 16.
  • the opening area characteristic is determined by the first surface 30, and the fluctuation of the valve opening (opening area of the communication passage) with respect to the pressure fluctuation (change of valve lift) in the high-pressure space becomes small.
  • the second surface 31 reaches the open end face of the communication passage, the fluctuation in the degree of instinct (opening area of the communication passage) with respect to the pressure fluctuation in the high-pressure space (change in valve lift) becomes large.
  • the opening area is increased up to the opening area corresponding to the passage cross section of FIG. 14, and it is possible to obtain the characteristics shown by the solid line (II line) in FIG. Therefore, when the expansion device 5 having such a valve element configuration is used, the valve element 17 is lifted in a region where the high pressure is reduced, that is, in a direction in which the opening area of the communication passage 14 is increased. In the initial stage, the fluctuation of the valve opening (opening area of the communication passage) with respect to the pressure fluctuation of the high-pressure space (change of valve lift) can be reduced, so that the capacity of the compressor 2 is reduced by the pressure of the low-pressure line.
  • valve element 1 of the expansion device 5 can be used. 7 can easily seat on the valve seat 16 and block the communication passage 31 even further, and intermittently occurs by suppressing a remarkable decrease in low pressure and a remarkable decrease in the discharge amount of the compressor 2. It is possible to suppress fluctuations in frozen cycle 1. Becomes ability, the cooling capacity at a low load current can be stabilized.
  • valve element 17 it is possible to adjust the opening area characteristic by processing the first surface 30. That is, according to the above-described configuration, an example in which the first surface 30 is formed flat has been described. However, the inclination angle (0 1) of the first surface 30 may be changed, or the first surface 30 may be changed. By forming 30 on a curved surface, etc., the pressure fluctuation in the high-pressure space at the beginning of the lift of the valve element 17 (valve lift) The change of the valve opening (opening area of the communication passage) with respect to the change of the valve can be set to a desired characteristic.
  • FIGS. 14 to 16 The configuration shown in FIGS. 14 to 16 described above is an example in which the valve 17 is lifted until the valve 17 is separated from the opening end face of the communication passage 14, but the valve 17 is lifted In this case, a guide piece continuously inserted into the communication passage may be provided on the valve element 17.
  • FIGS. 17 and 18 An example of such a configuration is shown in FIGS. 17 and 18.
  • a guide piece 35 extends from the tip of the face 31 in the axial direction of the valve element 17, and the guide face 32 extends behind the guide piece 35 to the tip of the guide piece 35.
  • the guide surface 32 is always in contact with the guide receiving portion 33 formed with the communication passage 14 regardless of the lift of the valve 17. ing.
  • Other configurations are the same as those shown in FIGS. 14 to 16, and therefore, the same portions are denoted by the same reference numerals and description thereof will be omitted.
  • the guide piece 35 inserted into the communication path 14 defines the maximum opening area of the communication path 14, and in this example, the maximum opening area is 1.5 to 3.0 mm in diameter. It is set to be about the same as a hole of about mm.
  • the first and second surfaces 30 and 31 define the opening area characteristics of the valve element 17 with respect to the lift.
  • the stroke amount of the valve 17 is almost proportional to the refrigerant pressure in the high-pressure space 11.
  • the opening area characteristics are determined by the first surface 30, and the valve opening degree (pressure change) with respect to the pressure fluctuation (change in valve lift) of the high-pressure space 11 is determined.
  • the opening area of the passage decreases, and then the second surface becomes the open end surface of the communication passage.
  • the valve opening degree opening area of the communication passage
  • the compressor 2 is of a variable capacity type whose capacity is controlled by the pressure of the low pressure line as the compressor 2, and this cycle is performed in a subcritical region where the high pressure is equal to or lower than the critical pressure.
  • the maximum opening area is a portion of the passage cross-section of the communication passage 14 excluding the portion occupied by the guide pieces 35, so that the portion occupied by the guide pieces 35 ( By adjusting the cross section of the guide piece, it is possible to adjust the opening area when fully opened.
  • the valve body 17 By the way, according to the above-described valve body structure, the position at which the opening area of the communication passage 14 is minimized by bringing the valve body 17 into contact with the valve seat 16 provided at the opening end of the communication passage 14.
  • the valve opening by adjusting the amount of insertion into the communication passage 14 of the valve body without providing a valve seat, the valve opening (communication Similarly, the opening area characteristics may be obtained by a spool type valve element that adjusts the opening area of the road. For example, to construct a spool-type valve structure using the valve element 17 shown in FIG. 17, as shown in FIG. 19, as shown in FIG. It is preferable that the valve body 17 be formed in accordance with the shape of the base end of the valve element 17 so that the opening area of the communication passage 14 can be minimized by the stopper 36.
  • the stopper 36 is formed, for example, in a cylindrical shape that is fixed integrally with the valve element 17 and is displaced with the movement of the valve element 17, and the valve element 17 enters the communication path 14.
  • the partition wall 13 is configured to abut around a portion where the communication passage 14 is opened to prevent further displacement of the valve element 17.
  • a notch is formed at an appropriate position on the side wall so that the flow of the refrigerant is not blocked. 7 should be formed.
  • the other configuration is the same as the configuration of the valve element shown in FIG. 17, and the same portions are denoted by the same reference numerals and description thereof will be omitted.
  • the opening area of the communication passage 14 is closed.
  • the movement of the valve element, that is, the position at which the opening area of the communication passage 14 is minimized is determined by the stop horn 36, so that the lower limit value of the included angle of the valve element 17, that is, The valve body shown in the figure can be freely set without considering the lower limit value of the included angle (inclination angle with respect to the axis) between the first surface 30 and the axis.
  • the non-electric type expansion device including the sensing element whose movement of the valve body is controlled according to the refrigerant condition on the radiator side has the smallest opening area of the communication path.
  • the valve body of the expansion device is made to have a characteristic of reducing the fluctuation of the opening area of the communication path due to the pressure fluctuation of the high-pressure space.
  • the communication path that connects the high pressure space and the low pressure space of the expansion device is formed. The characteristic of the valve opening area with respect to the high pressure is shown by the characteristic line in Fig.
  • the communication passage is formed as a through-hole having the same diameter from the high-pressure space to the low-pressure space, and the change in the diameter per unit axial direction is continuously changed at an equal rate from the base to the tip of the valve body. It is formed in a shape of a truncated cone, and the tip of the valve is separated from the open end of the communication passage while the valve is lifted from the position where the opening area is minimum to the position where it is maximum. Therefore, or alternatively, gradually reduce the diameter of the valve body toward the tip A first conical portion, and a second conical portion that is formed on the distal end side of the first conical portion and gradually decreases in diameter toward the distal end.
  • the angle of the included angle between the bus line of the conical portion and the axis of the valve body is smaller than the angle of the included angle between the bus line of the first conical portion and the communication passage.
  • a first conical path formed at an angle larger than the angle of the included angle between the axis of the valve body and the generatrix of the first conical portion; and an axis of the communication passage formed following the first conical path and formed with the first conical path.
  • a second conical path in which the angle of the included angle is smaller than the angle of the included angle between the axis of the valve body and the generatrix of the second conical portion.
  • the valve body has a first surface formed with a predetermined angle between the axis and the axis thereof, and a first surface formed further from the first surface than the first surface and formed with the axis of the valve body.
  • the fluctuation of the valve opening can be reduced, and at low load where the valve opening (opening area of the communication passage) decreases, the expansion device can be easily closed due to pressure fluctuation. Avoid inconveniences that occur intermittently Flip obtain low load cycle variations occur difficulty comb at the time, the cooling capacity at a low load current can be stabilized with.
  • the communication passage may be provided. Maximum opening area without changing the shape of the communication passage It is also possible to cut the side surface of the valve body in the axial direction to form a guide surface, and to form a guide receiving surface for receiving this guide surface in the communication passage. If this is the case, it becomes possible to easily position the valve element.
  • the valve body having the first surface and the second surface the valve having the smallest opening area by seating the first surface of the valve body on the valve seat formed at the end of the communication passage.
  • a stopper that displaces integrally with the valve body is provided, and the stopper defines the position of the valve body that minimizes the opening area. It is possible to adopt a type of seating on a valve seat or a spool type valve.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Temperature-Responsive Valves (AREA)

Abstract

Un dispositif de détente (5) utilisé dans un cycle frigorifique comprend une caractéristique permettant de réduire une variation de la zone d'ouverture liée à une fluctuation de la pression dans un espace à haute pression au début de la remontée d'un disque de soupape depuis une position dans laquelle une zone d'ouverture d'un chemin de communication devient minimale; le disque (17) de soupape pouvant être réalisé avec une forme ayant cette même caractéristique pour permettre à une variation de l'ouverture de la soupape en relation avec une fluctuation de la pression dans l'espace (11) à haute pression de diminuer en même temps que diminue la zone d'ouverture du chemin (14) de communication ou bien, au lieu d'ajuster la forme du disque (17) de soupape, ce dernier (17) peut être réalisé avec une forme telle qu'une variation de l'ouverture de la soupape liée à une fluctuation de la pression dans l'espace (11) à haute pression diminue lorsque diminue la zone d'ouverture du chemin (14) de communication, ceci permettant d'éviter une variation intermittente des cycles dans des conditions de faible charge dans un cycle frigorifique comprenant un frigorigène à point critique faible tel que le CO2.
PCT/JP2000/006900 1999-10-08 2000-10-04 Cycle frigorifique WO2001027543A1 (fr)

Applications Claiming Priority (4)

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JP11/287513 1999-10-08
JP28751399 1999-10-08
JP2000/275761 2000-09-12
JP2000275761A JP2001174076A (ja) 1999-10-08 2000-09-12 冷凍サイクル

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1265041A2 (fr) * 2001-06-07 2002-12-11 TGK Co., Ltd. Cycle frigorifique
FR2863695A1 (fr) * 2003-12-16 2005-06-17 Otto Egelhof Gmbh & Co Kg Vanne de coupure, ensemble a vanne de coupure, et vanne de detente pour des installations frigorifiques
FR2867261A1 (fr) * 2004-03-03 2005-09-09 Otto Egelhof Gmbh & Co Kg Vanne de detente et procede pour sa commande
FR2868830A1 (fr) * 2004-04-09 2005-10-14 Valeo Climatisation Sa Dispositif de detente ameliore pour circuit de climatisation
EP1722175A2 (fr) * 2005-05-12 2006-11-15 Behr GmbH & Co. KG Soupape à pression différentielle
US7246501B2 (en) 2003-12-16 2007-07-24 Otto Egelhof Gmbh & Co. Kg Shut-off valve, kit having a shut-off valve, and an expansion valve
EP1832819A1 (fr) * 2004-11-26 2007-09-12 Valeo Thermal Systems Japan Corporation Cycle de réfrigération
EP1722176A3 (fr) * 2005-05-13 2007-09-19 Behr GmbH & Co. KG Soupape à pression différentielle
EP2883723A1 (fr) * 2013-12-13 2015-06-17 Valeo Systemes Thermiques Procédé de conditionnement thermique d'un habitacle d'un véhicule automobile
WO2020259901A1 (fr) * 2019-06-27 2020-12-30 Danfoss A/S Procédé de création d'une variance de capacité maximale d'un détendeur

Families Citing this family (4)

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FR2862573B1 (fr) * 2003-11-25 2006-01-13 Valeo Climatisation Installation de climatisation de vehicule
EP1857747A1 (fr) * 2005-02-24 2007-11-21 Denso Corporation Soupape de regulation de pression
JP2008064439A (ja) * 2006-09-11 2008-03-21 Daikin Ind Ltd 空気調和装置
JP6639876B2 (ja) * 2015-11-17 2020-02-05 株式会社不二工機 流量調整弁

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JPH0113882Y2 (fr) * 1981-02-18 1989-04-24
WO1990007683A1 (fr) * 1989-01-09 1990-07-12 Sinvent As Dispositif a cycle de carnot renverse en conditions transcritiques
WO1993006423A1 (fr) * 1991-09-16 1993-04-01 Sinvent A/S Procede de regulation de pression en partie haute dans un dispositif a cycle de carnot renverse transcritique
WO1994014016A1 (fr) * 1992-12-11 1994-06-23 Sinvent A/S Dispositif de compression trans-critique de vapeur
JPH09133435A (ja) * 1995-11-08 1997-05-20 Mitsubishi Heavy Ind Ltd 膨脹弁
EP0786632A2 (fr) * 1996-01-25 1997-07-30 Denso Corporation Système de réfrigération avec soupape de commande de pression
EP0837291A2 (fr) * 1996-08-22 1998-04-22 Denso Corporation Système frigorifique du type à compression de vapeur
JPH11248272A (ja) * 1998-01-05 1999-09-14 Denso Corp 超臨界冷凍サイクル
JP2000097523A (ja) * 1998-09-24 2000-04-04 Zexel Corp 超臨界冷凍サイクルの膨張装置
EP1001229A2 (fr) * 1998-11-12 2000-05-17 Ford-Werke Aktiengesellschaft Elément d'expansion et unité de soupape à utiliser avec cet élément

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JPH0113882Y2 (fr) * 1981-02-18 1989-04-24
WO1990007683A1 (fr) * 1989-01-09 1990-07-12 Sinvent As Dispositif a cycle de carnot renverse en conditions transcritiques
WO1993006423A1 (fr) * 1991-09-16 1993-04-01 Sinvent A/S Procede de regulation de pression en partie haute dans un dispositif a cycle de carnot renverse transcritique
WO1994014016A1 (fr) * 1992-12-11 1994-06-23 Sinvent A/S Dispositif de compression trans-critique de vapeur
JPH09133435A (ja) * 1995-11-08 1997-05-20 Mitsubishi Heavy Ind Ltd 膨脹弁
EP0786632A2 (fr) * 1996-01-25 1997-07-30 Denso Corporation Système de réfrigération avec soupape de commande de pression
EP0837291A2 (fr) * 1996-08-22 1998-04-22 Denso Corporation Système frigorifique du type à compression de vapeur
JPH11248272A (ja) * 1998-01-05 1999-09-14 Denso Corp 超臨界冷凍サイクル
JP2000097523A (ja) * 1998-09-24 2000-04-04 Zexel Corp 超臨界冷凍サイクルの膨張装置
EP1001229A2 (fr) * 1998-11-12 2000-05-17 Ford-Werke Aktiengesellschaft Elément d'expansion et unité de soupape à utiliser avec cet élément

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1265041A3 (fr) * 2001-06-07 2004-03-17 TGK Co., Ltd. Cycle frigorifique
EP1265041A2 (fr) * 2001-06-07 2002-12-11 TGK Co., Ltd. Cycle frigorifique
US7246501B2 (en) 2003-12-16 2007-07-24 Otto Egelhof Gmbh & Co. Kg Shut-off valve, kit having a shut-off valve, and an expansion valve
FR2863695A1 (fr) * 2003-12-16 2005-06-17 Otto Egelhof Gmbh & Co Kg Vanne de coupure, ensemble a vanne de coupure, et vanne de detente pour des installations frigorifiques
FR2867261A1 (fr) * 2004-03-03 2005-09-09 Otto Egelhof Gmbh & Co Kg Vanne de detente et procede pour sa commande
FR2868830A1 (fr) * 2004-04-09 2005-10-14 Valeo Climatisation Sa Dispositif de detente ameliore pour circuit de climatisation
US7243501B2 (en) 2004-04-09 2007-07-17 Valeo Climatisation Expansion device for an air-conditioning system
EP1715264A1 (fr) * 2004-04-09 2006-10-25 Valeo Systèmes Thermiques Dispositif de détente améliorée pour circuit de climatisation
EP1832819A1 (fr) * 2004-11-26 2007-09-12 Valeo Thermal Systems Japan Corporation Cycle de réfrigération
EP1832819A4 (fr) * 2004-11-26 2014-10-22 Valeo Thermal Sys Japan Co Cycle de réfrigération
EP1722175A2 (fr) * 2005-05-12 2006-11-15 Behr GmbH & Co. KG Soupape à pression différentielle
EP1722175A3 (fr) * 2005-05-12 2007-09-19 Behr GmbH & Co. KG Soupape à pression différentielle
EP1722176A3 (fr) * 2005-05-13 2007-09-19 Behr GmbH & Co. KG Soupape à pression différentielle
EP2883723A1 (fr) * 2013-12-13 2015-06-17 Valeo Systemes Thermiques Procédé de conditionnement thermique d'un habitacle d'un véhicule automobile
FR3014756A1 (fr) * 2013-12-13 2015-06-19 Valeo Systemes Thermiques Procede de conditionnement thermique d'un habitacle d'un vehicule automobile
WO2020259901A1 (fr) * 2019-06-27 2020-12-30 Danfoss A/S Procédé de création d'une variance de capacité maximale d'un détendeur

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