WO2012146193A1 - 热力膨胀阀 - Google Patents

热力膨胀阀 Download PDF

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Publication number
WO2012146193A1
WO2012146193A1 PCT/CN2012/074790 CN2012074790W WO2012146193A1 WO 2012146193 A1 WO2012146193 A1 WO 2012146193A1 CN 2012074790 W CN2012074790 W CN 2012074790W WO 2012146193 A1 WO2012146193 A1 WO 2012146193A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure receiving
thermal expansion
pressure
receiving surface
Prior art date
Application number
PCT/CN2012/074790
Other languages
English (en)
French (fr)
Inventor
刘长青
Original Assignee
浙江三花股份有限公司
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 浙江三花股份有限公司 filed Critical 浙江三花股份有限公司
Priority to US14/113,574 priority Critical patent/US9587864B2/en
Priority to EP12776448.8A priority patent/EP2703751B1/en
Publication of WO2012146193A1 publication Critical patent/WO2012146193A1/zh

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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
    • 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
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
    • 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
    • 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
    • F25B2341/064—Superheater 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
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature

Definitions

  • the invention relates to the technical field of refrigerant fluid control components, and in particular to a thermal expansion valve. Background technique
  • the thermal expansion valve is an important component of the refrigeration system and is another essential component in the four basic components of the refrigeration system, except for the evaporator, compressor and condenser.
  • the main function of the thermal expansion valve is to control the opening degree of the valve through the superheat of the evaporator outlet end or the compressor suction end of the induction refrigeration system, thereby achieving the purpose of system refrigerant flow regulation and throttling.
  • FIG. 1 is a schematic structural view of a typical thermal expansion valve in the prior art.
  • the thermal expansion valve includes a valve body ⁇ , and the upper end of the valve body 1' is connected with a gas box including a gas box seat 2'4 and a gas box cover 2'5, and the inner chamber of the gas box is divided into an upper chamber 2' by a diaphragm 2' 2 and the lower chamber 2'3; as shown in Fig.
  • the upper chamber 2'2 is filled with refrigerant and connected to the temperature sensing package 4'2 through the capillary 4, and the temperature sensing package 4'2 is used to sense the outlet end of the evaporator or to compress The superheat of the refrigerant at the inlet end of the machine, and a temperature pressure P b is generated in the upper chamber; at the same time, the lower chamber 2'3 communicates with the outlet end of the evaporator through a balance tube (not shown), thereby being in the lower chamber 2 An evaporation pressure P is generated in '3. .
  • a valve port 1 ⁇ is formed in the inner cavity of the valve body 1 ′, the valve port 1 ⁇ is fitted with a valve core 3 ⁇ , and the upper end of the valve core 3 ⁇ is connected with a transmission rod 3 ′ 2 , the transmission rod 3 ′ 2 is connected with a transmission piece 3'3 located in the lower chamber;
  • the valve core 3, the transmission rod 3'2 and the guide ball 3'4 described below are collectively referred to as a valve core member.
  • the valve core member is a separate component; the outer portion of the valve core 3 ⁇ is provided with a guide ring 7', and the cavity below the guide ring 7' is a balance chamber 1'4, the balance chamber 1'4 There is a spring 6' supporting the spool 3', which springs the spool 3 with an upward elastic force Pt .
  • valve core 3 ⁇ and the transmission rod 3'2 as the force analysis object, the valve core 3 ⁇ and the transmission rod 3'2 are subjected to To an upward elastic force P t , at the same time, it is subjected to the downward thrust given by the transmission piece 3'3, and the thrust is formed by the diaphragm 2 ⁇ pushing the transmission piece 3'3, so that the thrust also causes the diaphragm 2 to move downward.
  • Force, ie P b -P. P t
  • ie P b P.
  • the spool 3 is subjected to the above-mentioned temperature pressure P b and evaporation pressure P.
  • the pressure generated by the refrigerant in the first interface chamber 1 '2 to open the spool 3 ⁇ and the pressure in the second interface chamber 1 ′ 3 to close the spool 3 are also applied.
  • the difference produces a system pressure difference; for small volume valves or low pressure refrigeration systems, the differential pressure of the system has a negligible effect on the spool 3 ⁇ , but for high volume valves or high pressure refrigeration systems, the system The differential pressure has a great influence on the spool 3 ⁇ , which seriously affects the adjustment accuracy of the spool 3 ⁇ .
  • the valve core 3 defines a through hole 3 ⁇ 1 communicating with the first interface cavity 1′2 and the balance cavity ⁇ 4, and the lower end of the through hole 3 ⁇ 1 is matched with a guiding ball 3′4, the guiding ball 3′4
  • the force receiving area of the surface S'2 is equal. Since the force directions of the first pressure receiving surface S'l and the second pressure bearing surface S'2 are opposite, the refrigerant in the first interface chamber 1'2 is generated to the valve core 3'.
  • the second interface chamber 1'3 is provided with a third bearing surface S'3 and a fourth bearing surface S'4, which are opposite in direction of force, due to the two The force receiving areas of the pressure receiving faces are equal, so that the pressure generated by the refrigerant in the second interface chamber 1'3 against the spool 3 ⁇ cancels each other. Therefore, whether the refrigerant flows from the first interface chamber 1'2 to the second interface chamber 1'3 or from the second interface chamber 1'3 to the first interface chamber 1'2, the system pressure difference is substantially zero, and thus the thermal expansion valve A two-way balanced flow can be achieved.
  • a first sealing member 8' is disposed between 1' for isolating the first interface chamber 1'2 and the lower chamber 2'3; and a second sealing member 8'2 is disposed between the valve core 3' and the guide ring 7'.
  • the second interface chamber 1'3 and the balance chamber 1'4 are isolated; the transmission rod 3'2 and the spool 3' are axially moved, so that the above two seals are transmission seals, and the following defects exist:
  • the frictional resistance of the transmission seal is large, and as the use time prolongs, the aging of the rubber, the frictional resistance may further increase, thereby affecting the sensitivity of the thermal expansion valve;
  • the precision of the cooperation between the valve body 1' and the transmission rod 3'2 and between the valve core 3A and the guide ring 7' is high, the valve body 1', the transmission rod 3'2, the valve core 3" and the guide ring 7 'The processing is difficult; if the valve body 1' and the transmission rod 3'2 and between the valve core 3 ⁇ and the guide ring 7' are not sealed by a seal, but a high-precision fit seal, the valve body 1' The transmission rod 3'2, the valve core 3 ⁇ and the guide ring 7' are more difficult to process.
  • the second pressure receiving surface S'2 is disposed on the lower end surface of the valve body 3 ⁇
  • the lower end surface of the valve core 3 ⁇ is located in the balance chamber 1'4, so that a through hole 3 ⁇ 1 is required to be opened on the valve core 3 ⁇ .
  • the interface chamber 1'2 and the balance chamber 1'4 are such that the pressures in the two chambers are equal; on this basis, the guide ball 3'4 is required to be provided at the lower end of the spool through hole, and at the same time, for the purpose of facilitating the valve core 3
  • the through hole 3 ⁇ 1 is opened, and the split structure design of the transmission rod 3'2 and the valve core 3 ⁇ is adopted.
  • the valve core member includes the transmission rod 3'2, the valve core 3 ⁇ , and the guiding ball 3'4,
  • the number of components is large, resulting in a large cumulative axial dimension tolerance, which reduces the adjustment accuracy of the valve, and the assembly is troublesome;
  • the balance chamber 1'4 is in communication with the first interface chamber 1'2.
  • the first interface chamber 1'2 is a high pressure end
  • the pressure in the balance chamber 4 is high, resulting in high sealing requirements and increased leakage.
  • the through hole 3 ⁇ 1 is provided on the smaller valve core 3 ⁇ , which is difficult to process.
  • the technical problem to be solved by the present invention is to provide a thermal expansion valve, and the structural design of the thermal expansion valve can improve the reliability of sealing between the valve body and the upper end portion of the valve core member, and improve the reliability.
  • the sensitivity of the valve can reduce the processing difficulty of the valve body and the valve core component; on the other hand, it can eliminate the pressure influence of the refrigerant in the first interface cavity on the movement of the valve core component.
  • the present invention provides a thermal expansion valve including a valve body and a valve core member, the valve body being provided with a first interface chamber, a lower chamber in which a transmission member is built, and a first sealing member that isolates both
  • the side wall of the valve core member is provided with a fifth pressure receiving surface and a sixth pressure receiving surface which are subjected to the pressure of the refrigerant in the first interface chamber and are opposite in the direction of the force;
  • the first sealing member is disposed on the side wall a first flexible sealing member between the transmission member and the upper end portion of the valve core member and the first edge portion thereof is sealingly connected to the valve body;
  • the first pressure receiving surface of the first flexible sealing member The sum of the effective force receiving area and the force receiving area of the fifth bearing surface is substantially equal to the effective force receiving area of the third pressure receiving surface of the upper end portion of the valve core member and the force of the sixth pressure receiving surface The sum of the areas.
  • an effective force receiving area of the first pressure receiving surface is substantially equal to an effective force receiving area of the third pressure receiving surface, and a force receiving area of the fifth pressure receiving surface is substantially equal to the sixth pressure receiving surface The area of force.
  • the fifth pressure receiving surface and the sixth pressure receiving surface are both opened in the first interface cavity.
  • the wide body is further provided with a second interface cavity, a balance cavity with a built-in elastic component and a second sealing component for isolating the two, and on the sidewall of the valve core component in the second interface cavity a seventh pressure receiving surface and an eighth pressure receiving surface opposite to each other;
  • the second sealing member is disposed between the elastic member and the lower end portion of the wide core member and has a second edge portion sealed and connected a second flexible seal on the valve body; a sum of an effective force receiving area of the second pressure receiving surface of the second flexible sealing member and a force receiving area of the seventh bearing surface, substantially equal to a sum of an effective force receiving area of the fourth pressure receiving surface of the lower end portion of the valve core member and a force receiving area of the eighth pressure receiving surface.
  • an effective force receiving area of the second pressure receiving surface is substantially equal to an effective force receiving area of the fourth pressure receiving surface, and a force receiving area of the seventh pressure receiving surface is substantially equal to the eighth pressure receiving surface The area of force.
  • valve body is provided with a valve port
  • valve core member is provided with an inclined sealing surface for sealing the valve port
  • sealing line or sealing surface when the valve core member closes the valve port separates the inclined sealing surface
  • the first flexible seal is a first bellows;
  • the first bellows includes a first corrugated sleeve portion that is expandable and contractable in the axial direction, and a first straight portion that closes the first corrugated sleeve portion from one end a segment portion; an upper end portion of the wide core member projects into the first corrugated sleeve portion, and an upper end surface thereof is in contact with an inner side surface of the first straight portion.
  • the transmission component includes a transmission piece and a transmission pin connected to the transmission piece, and the first straight section is disposed between the transmission nail and the upper end of the valve core component, and the The outer side of the straight section is in contact with the bottom wall of the drive pin.
  • a top end portion of the wide body is provided with a mounting hole for mounting the first flexible sealing member, and a nut is screwed into the mounting hole; the nut is fitted to the first corrugated sleeve through an inner hole thereof a cylindrical portion and an outer portion of the driving nail, and pressing the first edge portion against a bottom wall of the mounting hole; and sealingly connecting the first edge portion with a bottom wall of the mounting hole.
  • the circumferential end of the first edge portion is further provided with a first flange, and the bottom end of the side wall of the mounting hole is provided with a groove opposite to the first flange position;
  • the flange extends into the recess and snaps onto the outer sidewall of the nut.
  • the first seal always isolates the lower chamber from the first interface chamber; and in particular, the sealing between the first edge portion and the valve body may be a hermetic seal or a seal sealing isostatic seal.
  • the seal between the first edge portion and the valve body in the present invention is a static seal structure, the reliability of the seal is high, and the probability of leakage is low, so that the thermal expansion valve is not increased. Superheat, which significantly improves the reliability and accuracy of thermal expansion valve operation.
  • the sealing structure exists between the first edge portion and the valve body, not between the valve core member and the valve body, so that the spool member is not subjected to frictional resistance during the axial movement. The effect of the valve is therefore higher.
  • the first edge portion and the valve body are in a static sealing structure instead of the prior art transmission sealing structure, so that the processing precision of the valve body and the valve core member is not high, and can be remarkable Reduce the difficulty of processing.
  • an effective force receiving area of the first pressure receiving surface of the first flexible sealing member and the fifth The sum of the force receiving areas of the pressure receiving surface is substantially equal to the sum of the effective force receiving area of the third pressure receiving surface of the upper end portion of the valve core member and the force receiving area of the sixth pressure receiving surface, thereby eliminating the first The pressure exerted by the refrigerant in the interface cavity on the spool components.
  • the thermal expansion valve provided by the present invention can improve the reliability of sealing between the valve body and the upper end portion of the valve core member, improve the sensitivity of the valve, and can reduce the processing difficulty of the valve body and the valve core member; On the one hand, it can eliminate the pressure influence of the refrigerant in the first interface cavity on the movement of the valve core component.
  • FIG. 1 is a schematic structural view of a typical thermal expansion valve in the prior art
  • FIG. 2 is a schematic structural view of a thermal expansion valve according to an embodiment of the present invention.
  • Figure 3 is an enlarged view of a portion A of the thermal expansion valve of Figure 2;
  • Figure 4-1 is an illustration of the effective force area of the first bellows of Figures 2 and 3 under the first condition
  • Figure 4-2 is an illustration of the effective force area of the first bellows of Figures 2 and 3 under the second operating condition
  • Figure 5 is an enlarged view of a portion B of the thermal expansion valve of Figure 2;
  • Figure 6 is a schematic structural view of the second bellows of Figures 2 and 5;
  • Figure 7 is a schematic structural view of a valve core member of the thermal expansion valve of Figure 2;
  • Figure 7-1 is a plan view of the thermal expansion valve of Figure 7;
  • Figure 7-2 is a bottom view of the thermal expansion valve of Figure 7;
  • Figure 7-3 is a cross-sectional view taken along line A-A of the thermal expansion valve of Figure 7;
  • Figure 7-4 is a cross-sectional view taken along line B-B of the thermal expansion valve of Figure 7;
  • Figure 7-5 is a cross-sectional view taken along line C-C of the thermal expansion valve of Figure 7.
  • valve body 1 ⁇ valve port; 1'2 first interface cavity; 1'3 second interface cavity; 1'4 balance cavity;
  • 3 ⁇ spool 3 ⁇ 1 through hole; 3'2 transmission rod; 3'3 transmission piece; 3'4 guide ball;
  • valve body 11 first interface cavity; 12 second interface cavity; 13 balance cavity; 14 mounting hole; 141 groove; 15 nut; 16 first inner step surface; 17 second inner step surface;
  • gas box 31 gas box seat; 32 gas box cover; 33 diaphragm; 34 upper chamber; 35 lower chamber;
  • first bellows 41 first edge portion; 42 first corrugated sleeve portion; 43 first straight portion; 44 first flange; 45 first seal;
  • the core of the present invention is to provide a thermal expansion valve.
  • the structural design of the thermal expansion valve can improve the reliability of the sealing between the valve body and the upper end portion of the valve core member, improve the sensitivity of the valve, and reduce the valve body and The processing difficulty of the valve core component; on the other hand, it can eliminate the pressure influence of the refrigerant in the first interface chamber on the movement of the valve core component.
  • FIG. 2 is a schematic structural view of a thermal expansion valve according to an embodiment of the present invention
  • FIG. 3 is an enlarged view of a portion A of the thermal expansion valve of FIG. 2
  • FIG. 3 is a schematic view of the effective force receiving area of the first bellows in the first working condition
  • FIG. 4-2 is the effective force receiving area of the first bellows in the second working condition in FIGS. 2 and 3.
  • schematic diagram
  • the inner cavity of the body 1 is divided into a first interface cavity 11 and a second interface cavity 12;
  • the valve body 1 is connected with a gas box 3
  • the air box 3 includes a gas box seat 31, a gas box cover 32, and the inner cavity of the gas box 3 is separated
  • the diaphragm 33 of the upper chamber 34 and the lower chamber 35 is further provided with a transmission member 21 in the air box 3;
  • the thermal expansion valve further includes a first sealing member that isolates the first interface chamber 11 from the lower chamber 35.
  • the first sealing member further includes a first flexible sealing member that can be expanded and contracted with the movement of the valve core member 2, and the first flexible sealing member is disposed on the transmission member 21 and The upper end portion of the spool member 2 is sealed to the valve body 1 with its first edge portion 41.
  • the first flexible seal As the spool member 2 moves in the axial direction, the first flexible seal also expands and contracts in the axial direction, and its first edge portion 41 is sealingly coupled to the valve body 1, so that the first flexible seal will always be lowered
  • the cavity 35 is isolated from the first interface cavity 11; and in particular, the sealing between the first edge portion 41 and the valve body 1 may be a hermetic seal or a seal sealing isostatic seal.
  • the seal between the first edge portion 41 and the valve body 1 in the present invention is a static sealing structure, the sealing reliability is high, the probability of leakage is low, and thus the heat is not increased.
  • the superheat of the expansion valve significantly improves the reliability and accuracy of the operation of the thermal expansion valve.
  • the sealing structure exists between the first edge portion 41 and the valve body 1, rather than between the spool member 2 and the valve body 1, and thus the spool member 2 is moved in the axial direction. It is not affected by the frictional resistance, so the sensitivity of the valve is high. Furthermore, in the present invention, the first edge portion 41 and the valve body 1 are in a static sealing structure instead of the prior art transmission sealing structure, so that the machining accuracy of the valve body 1 and the valve core member 2 is not required. High can significantly reduce the difficulty of processing.
  • the sum of the effective force receiving area of the first pressure receiving surface S1 of the first flexible sealing member and the force receiving area of the fifth pressure receiving surface S5 is substantially equal to the third pressure receiving surface S3 of the upper end portion of the valve core member 2.
  • the sum of the effective force receiving area and the force receiving area of the sixth pressure receiving surface S6 can eliminate the pressure influence of the refrigerant in the first interface chamber 11 on the valve core member 2.
  • first bellows 4 will be taken as an example to explain the effective force receiving area of the first pressure receiving surface S1 of the first flexible sealing member:
  • the working condition determines the effective force receiving area of the first bearing surface S1.
  • the first working condition is as follows: As shown in FIG.
  • the first edge portion 41 is only in contact with the bottom wall of the mounting hole 14, but is not connected, so there is no force between the two; under the working condition
  • Each corrugation in the first bellows 4 is subjected to two pressures of opposite ⁇ , as shown by the arrows in Fig. 4-1, so that the effective stress area of the first bellows is A S11 in Fig. 4. Shown.
  • the second working condition is as follows: as shown in FIG.
  • the effective force receiving area of the first pressure receiving surface S1 can be substantially equal to the effective force receiving area of the third pressure receiving surface S3, and the force receiving area of the fifth pressure receiving surface S5 is substantially equal to the force of the sixth pressure receiving surface S6. area.
  • a S12 is closer to the area of the upper end surface of the valve core member 2.
  • the effective force receiving area of a pressure receiving surface S1 is substantially equal to the effective force receiving area of the third pressure receiving surface S3.
  • valve body 1 is provided with a valve port 18, the valve core member 2 is provided with an inclined sealing surface of the sealing valve port 18, and the sealing line or sealing surface when the valve core member 2 closes the valve port 18 is separated.
  • the inclined sealing surface is a sixth pressure receiving surface S6 in the first interface chamber 11 and a seventh pressure receiving surface S7 in the second interface chamber 12.
  • the balance chamber 13 is further separated from the first interface chamber 11 Sealed, and a fifth pressure receiving surface opposite to the direction of the force of the sixth pressure receiving surface S6 is further formed on the side wall of the valve member 2 in the first interface chamber 11.
  • the fifth pressure receiving surface S5 is opened in the first interface cavity 11 instead of being opened in the balance chamber 13, so that the through hole is not provided in the valve core member 2 for communicating the first interface cavity 11 and the balance cavity. 13 , and further avoiding the use of the guiding ball at the lower end of the through hole, omitting the guiding ball member, thereby reducing the number of components of the valve core member 2, ensuring the axial dimensional tolerance thereof, and improving the adjustment precision of the valve.
  • the through hole is not formed in the valve body member 2, the machining process of the valve core member 2 is also compressed, which reduces the processing difficulty.
  • the balance chamber 13 is further sealed from the first interface chamber 11, when the first interface chamber 11 is the high pressure end, the balance chamber 13 is always kept at a low pressure, and the balance chamber 13 is simultaneously isolated from the second interface chamber 12. Sealed, so that there is substantially no refrigerant present in the balance chamber 13, thus significantly reducing the sealing requirements of the balance chamber 13.
  • FIG. 2 is an enlarged view of the B portion of the thermal expansion valve
  • Fig. 6 is a schematic view showing the structure of the second bellows of Figs. 2 and 5.
  • the valve body 1 is further provided with a second interface chamber 12, a balance chamber 13 with a built-in elastic member 22, and a second sealing member for isolating both, and in the second interface chamber 12, the spool member 2 a seventh pressure receiving surface S7 and an eighth pressure receiving surface S8 having opposite force directions are disposed on the side wall; on the basis of the second sealing member, the second sealing member is disposed on the elastic member 22 and the wide core a second flexible seal between the lower end of the component 2 and the second edge portion 51 thereof is sealingly connected to the valve body 1; the technical effect of the second flexible seal is substantially the same as that of the first flexible seal, This will not be repeated here.
  • the sum of the effective force receiving area of the second pressure receiving surface S2 of the second flexible sealing member and the force receiving area of the seventh bearing surface S7 is substantially equal to the fourth bearing surface of the lower end portion of the valve core member 2
  • the sum of the effective force receiving area of S4 and the force receiving area of the eighth bearing surface S8 thus eliminating the second connection on the basis of eliminating the influence of the pressure of the refrigerant on the valve core member 2 in the first interface chamber 11
  • the system pressure difference is basically zero, so the thermal expansion valve can achieve two-way flat Balance the flow.
  • the second pressure receiving surface S2, the fourth pressure receiving surface S4, the seventh pressure receiving surface S7 and the eighth pressure receiving surface S8 are easily calculated, and the second pressure receiving surface S2 can be made
  • the effective force receiving area is substantially equal to the effective bearing area of the fourth bearing surface S4, and the force receiving area of the seventh bearing surface S7 is substantially equal to the force receiving area of the eighth bearing surface S8.
  • the specific structure of the first flexible seal can also be designed.
  • the first flexible seal may specifically be a first bellows 4, and the first bellows 4 includes a first corrugated sleeve portion 42 and a first straight portion 43, a first corrugated sleeve
  • the tubular portion 42 can be telescoped in the axial direction, and the first straight portion 43 closes the first corrugated sleeve portion 42 at the top end such that the opening of the first wave sleeve portion 42 faces downward; on this basis,
  • the upper end portion of the valve body member 2 projects into the first corrugated sleeve portion 42, and its upper end surface is fitted to the inner side surface of the first straight portion portion 43.
  • the first bellows portion 42 is elongated or compressed in the axial direction, and the regularity of the expansion and contraction is high, thereby having high work reliability. Further, since the upper end surface of the spool member 2 is fitted to the inner side surface of the first straight portion 43, the force transmission is more advantageous.
  • the transmission member 21 includes a transmission piece 211 and a transmission pin 212 connected to the transmission piece 211, and the first straight portion 43 is further provided at the upper end portion of the transmission pin 212 and the valve core member 2.
  • the outer side surface of the first straight portion 43 is in contact with the bottom wall of the driving nail 212.
  • the contact area of the first straight portion 43 with the driving pin 212 should be as large as possible, so that the first The outer side of the straight section 43 can cover all or substantially all of the bottom wall of the drive pin 212.
  • the top end portion of the valve body 1 is provided with a mounting hole 14 for arranging the first bellows 4, and the mounting hole 14 is internally threaded with a nut 15;
  • the nut 15 is fitted to the first corrugated sleeve portion 42 and the transmission through the inner hole thereof.
  • the outer portion of the nail 212 presses the first edge portion 41 against the bottom wall of the mounting hole 14; the first edge portion 41 is sealingly connected with the bottom wall of the mounting hole 14.
  • the fixing structure very conveniently realizes the fixed installation of the first bellows 4, and since the nut 15 and the mounting hole 14 are detachably threaded, the nut 15 can be removed after the first bellows 4 is damaged. , replace the first bellows 4. Further, the nut 15 presses the first edge portion 41 against the bottom wall of the mounting hole 14 with a certain torque, so that the sealing performance between the first edge portion 41 and the bottom wall of the mounting hole 14 can be further improved.
  • the circumferential end of the first edge portion 41 may further be provided with a first flange 44, as shown in FIG.
  • the bottom end portion of the side wall is provided with a recess 141 opposite to the position of the first flange 44.
  • the first flange 44 extends into the EJ slot 141 and is caught on the outer side wall of the nut 15.
  • first edge portion 41 may be sealingly welded to the bottom wall of the mounting hole 14, or the first edge portion 41 may be provided with a first sealing member 45 on the bottom wall of the mounting hole 14.
  • the specific structure of the second flexible seal can also be designed.
  • the second flexible seal is a second bellows 5
  • the second bellows 5 includes a second corrugated sleeve portion 52 that is expandable and contractable in the axial direction, and the second end is closed at the bottom end.
  • the second straight portion 53 of the bellows portion 52 on the basis of this, as shown in FIG. 6, the second straight portion 53 is sandwiched between the spring seat 221 and the lower end portion of the valve member 2.
  • the second corrugated sleeve portion 52 is elongated or compressed in the axial direction, and the regularity of the expansion and contraction is high, thereby having high operational reliability.
  • the lower end portion of the valve core member 2 projects from the top end into the second corrugated sleeve portion 52, and the lower end surface thereof is flat and fits against the inner side surface of the first straight portion 53 to further
  • the outer side surface of the second straight portion 53 is in contact with the top wall of the spring seat 221; specifically, as shown in FIG. 5, the top end of the spring seat 221 is provided with a groove body, and the second straight portion
  • the portion 53 is disposed in the groove body; on the basis of this, in order to make the force transfer more effectively and avoid the abnormal deformation of the second straight portion 53, the second straight portion 53 should have the largest contact area with the bottom wall of the groove body.
  • the outer side surface of the second straight portion 53 is entirely or substantially entirely covered with the bottom wall of the tank.
  • the fixing structure between the second edge portion 51 and the valve body 1 can also be specifically designed.
  • the lower end of the valve body 1 is fitted with an adjusting seat 6, and the valve body 1 is provided with an inner stepped surface.
  • the adjusting seat 6 is screwed into the internally threaded hole at the lower end of the valve body 1.
  • the second edge portion 51 is sandwiched between the top wall of the adjustment seat 6 and the inner step surface, and the second edge portion 51 is sealingly connected to the inner step surface.
  • a first gasket 61 and a second gasket 62 are further arranged in the axial direction between the top wall of the adjusting seat 6 and the inner step surface, and the inner step surface includes a first inner step surface 16 and a second inner step surface 17, the first spacer 61 is supported on the first inner step surface 16, and the second spacer 62 is supported on the second inner step surface 17; on the basis of The two edge portions 51 are further sandwiched between the first spacer 61 and the second spacer 62, and the second edge portion 51 is sealingly connected to the first inner step surface 16.
  • This structural design fixes the position of the second edge portion 51 by two spacers in a fixed manner, thereby preventing the second edge portion 51 from sealingly connecting with the valve body 1 due to the extrusion of the refrigerant. Causes damage and improves the stability and reliability of the work.
  • the first spacer 61 is disposed at the second corrugated sleeve portion with its inner hole
  • the outer end of the second spacer 62 extends radially inward beyond the inner end portion of the first spacer 61 and is fitted to the inner end portion of the second edge portion 51.
  • the structural design is such that the second spacer 62 substantially covers the second edge portion 51, so that the expansion and contraction of the second corrugated sleeve portion 52 is more regular, and the second corrugated sleeve portion is prevented from being greatly deformed during the expansion and contraction of the 52. , thereby improving the reliability of the work.
  • the circumferential end of the second edge portion 51 is further provided with a second flange 55 which is caught on the outer side wall of the first spacer 61.
  • first bellows 4 and the second bellows 5 may be further equal, and the first bellows 4 and the second bellows 5 are disposed oppositely, thus the first bellows 4 and the second The action of the bellows 5 on the spool member 2 is equal and opposite, so that no additional force is applied to the spool member 2.
  • FIG. 7 is the spool of the thermal expansion valve in Figure 2.
  • Figure 7-1 is a top view of the thermal expansion valve of Figure 7;
  • Figure 7-2 is a bottom view of the thermal expansion valve of Figure 7;
  • Figure 7-3 is a cross-sectional view of the thermal expansion valve of Figure 7 taken along the line AA;
  • Figure 7-4 is a cross-sectional view taken along line BB of the thermal expansion valve of Figure 7;
  • Figure 7-5 is a cross-sectional view taken along line CC of the thermal expansion valve of Figure 7.
  • the force receiving area of the third bearing surface S3 is A S3; as shown in Figure 7-2, the force receiving area of the fourth pressing surface S4 is A S4; as shown in Figure 7-3
  • the force receiving area of the fifth pressing surface S5 is A S5; as shown in Figure 7-4, the force receiving area of the sixth pressure receiving surface S6 is A S6 , and the force receiving area of the seventh pressure receiving surface S7 is A S7; As shown in Figure 7-5, the force receiving area of the eighth pressing surface S8 is A S8.

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  • Engineering & Computer Science (AREA)
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  • Lift Valve (AREA)
  • Details Of Valves (AREA)
  • Temperature-Responsive Valves (AREA)

Abstract

一种热力膨胀阀，包括阀体（1）和阀芯部件（2），所述阀体（1）设有第一接口腔（11）、内置有传动部件（21）的下腔（35）及隔离二者的第一密封部件；所述阀芯部件（2）的侧壁上设有受到所述第一接口腔（11）内的冷媒压力并受力方向相反的第五承压面（S5）和第六承压面（S6）；所述第一密封部件包括设于所述传动部件（21）与所述阀芯部件（2）上端部之间、并其第一边缘部（41）密封连接于所述阀体（1）上的第一柔性密封件；所述第一柔性密封件的第一承压面（S1）的有效受力面积与所述第五承压面（S5）的受力面积之和，基本等于所述阀芯部件（2）上端部的第三承压面（S3）的有效受力面积与所述第六承压面（S6）的受力面积之和。该热力膨胀阀的结构设计一方面能够提高阀体（1）与阀芯部件（2）上端部之间密封的可靠性，并提高阀的灵敏度，且能够降低阀体（1）与阀芯部件（2）的加工难度；另一方面能够消除第一接口腔（11）中冷媒对阀芯部件（21）运动造成的压力影响。

Description

热力膨胀阀 本申请要求于 2011 年 04 月 27 日提交中国专利局、 申请号为 201110106904.9、发明名称为"热力膨胀阀"的中国专利申请的优先权，其全 部内容通过引用结合在本申请中。 技术领域
本发明涉及冷媒流体控制部件技术领域， 特别涉及一种热力膨胀阀。 背景技术
热力膨胀阀是组成制冷系统的重要部件， 是制冷系统四个基本部件中 除去蒸发器、 压缩机和冷凝器之外的另一基本部件。 热力膨胀阀的主要作 用是通过感应制冷系统中蒸发器出口端或压缩机吸入端的过热度来控制阀 的开度大小， 从而实现系统冷媒流量调节和节流降压的目的。
请参考图 1 , 图 1为现有技术中一种典型的热力膨胀阀的结构示意图。 该热力膨胀阀包括阀体 Γ,阀体 1'的上端连接有包括气箱座 2'4和气箱 盖 2'5的气箱， 该气箱的内腔由膜片 2Ί分隔为上腔 2'2和下腔 2'3； 如图 1 所示， 上腔 2'2充满有冷媒并通过毛细管 4Ί与感温包 4'2连接，感温包 4'2 用于感受蒸发器出口端或者压缩机入口端的冷媒的过热度， 并在上腔中产 生一个温度压力 Pb; 同时， 下腔 2'3通过平衡管 （图中未示出 )与所述蒸 发器出口端连通， 从而在下腔 2'3中产生一个蒸发压力 P。。
此外， 如图 1所示， 阀体 1'的内腔中形成有阀口 1Ί , 该阀口 1Ί配合 有阀芯 3Ί , 阀芯 3Ί的上端连接有传动杆 3'2, 该传动杆 3'2连接有位于下 腔的传动片 3'3； 需要说明的是， 在本现有技术中， 阀芯 3Ί、 传动杆 3'2 和下文所述的导向球 3'4合称为阀芯部件， 因而本现有技术中阀芯部件为 一种分体部件； 阀芯 3Ί的外部套装有导向环 7',该导向环 7'以下的腔体为 平衡腔 1'4, 平衡腔 1'4中设有支撑阀芯 3Ί的弹簧 6', 该弹簧 6'给阀芯 3Ί 一个向上的弹力 Pt。
以阀芯 3Ί和传动杆 3'2作为受力分析对象， 阀芯 3Ί和传动杆 3'2受 到一个向上的弹力 Pt, 同时会受到传动片 3'3给予的向下的推力， 该推力 由膜片 2Ί推动传动片 3'3形成， 因而该推力亦即使得膜片 2Ί向下运动的 力， 亦即 Pb-P。； 当阀芯 3Ί处于平衡状态时， Pb-P。=Pt, 亦即 Pb= P。+ Pt, 当蒸发器出口端的温度过高时， Pb增大， 从而推动阀芯 3Ί 向下运动， 从 而增大冷媒的流量； 当蒸发器出口端的温度过低时， Pb减小， 从而推动阀 芯 3Ί向上运动， 从而减小冷媒的流量。
然而， 如图 1所示， 在实际工作过程中， 阀芯 3Ί除了会受到上述温 度压力 Pb、 蒸发压力 P。和弹簧弹力 Pt之外， 还会受到第一接口腔 1'2中冷 媒产生的使阀芯 3Ί开启的压力和第二接口腔 1'3中使阀芯 3Ί关闭的压力， 该两个压力的差值产生一个系统压差； 对于小容量阀或者低压制冷系统而 言， 该系统压差的对阀芯 3Ί 的影响基本可以忽略不计， 但是对于大容量 阀或者高压制冷系统而言， 该系统压差对阀芯 3Ί 的影响很大， 从而严重 影响着阀芯 3Ί的调节精度。
有鉴于此， 如图 1所示， 阀芯 3Ί开设通孔 3Ί1连通第一接口腔 1'2 和平衡腔 Γ4, 该通孔 3Ί1的下端配合有导向球 3'4, 该导向球 3'4与通孔 3Ί1之间具有间隙， 从而使得两个腔室的压力相等， 同时使得第一接口腔 1'2中的第一承压面 S'l与平衡腔 1'4中的第二承压面 S'2的受力面积相等， 由于第一承压面 S'l和第二承压面 S'2的受力方向相反， 因而第一接口腔 1'2中的冷媒对阀芯 3Ί产生的压力相互 4氏消；如图 2所示，第二接口腔 1'3 中设有受力方向相反的第三承压面 S'3和第四承压面 S'4 , 由于该两个承压 面的受力面积相等， 因而第二接口腔 1'3中的冷媒对阀芯 3Ί产生的压力相 互抵消。 因而， 冷媒无论由第一接口腔 1'2流向第二接口腔 1'3 , 还是由第 二接口腔 1'3流向第一接口腔 1'2, 系统压差基本为零， 因而热力膨胀阀可 以实现双向平衡流动。
然而， 在上述现有技术中， 如图 1所示， 传动杆 3'2的上端部与阀体
1'之间设有第一密封部件 8Ί ,用于隔离第一接口腔 1'2和下腔 2'3； 阀芯 3Ί 与导向环 7'之间设有第二密封部件 8'2, 用于隔离第二接口腔 1'3和平衡腔 1'4； 传动杆 3'2和阀芯 3Ί沿轴向运动， 因而上述两种密封均为传动密封， 存在有以下缺陷： 第一， 传动密封的密封性能不可靠， 随着使用时间的延长， 橡胶的老 化， 泄漏会加大， 进而会使得热力膨胀阀的过热度加大， 影响热力膨胀阀 工作的可靠性和精确性；
第二， 传动密封的摩擦阻力大， 且随着使用时间的延长， 橡胶的老化， 摩擦阻力可能会进一步加大， 从而影响热力膨胀阀的灵敏度；
第三， 阀体 1'与传动杆 3'2之间及阀芯 3Ί与导向环 7'之间的配合精度 要求高， 阀体 1'、 传动杆 3'2、 阀芯 3Ί和导向环 7'的加工难度大； 如若阀 体 1'与传动杆 3'2之间及阀芯 3Ί与导向环 7'之间不是采用密封件密封， 而 是采用高精度的配合密封， 则阀体 1'、 传动杆 3'2、 阀芯 3Ί和导向环 7'的 加工难度会更大。
此外， 上述现有技术中的热力膨胀阀还存在如下缺陷：
第一， 由于第二承压面 S'2设于阀芯 3Ί的下端面上， 阀芯 3Ί的下端 面位于平衡腔 1'4中，因而需要在阀芯 3Ί上开设通孔 3Ί1连通第一接口腔 1'2和平衡腔 1'4, 使得两个腔体中的压强相等； 在此基础上， 需要在阀芯 通孔的下端设置导向球 3'4, 同时为了便于在阀芯 3Ί上开设有通孔 3Ί1 , 采用了传动杆 3'2与阀芯 3Ί的分体结构设计， 因而在该现有技术中阀芯部 件包括传动杆 3'2、 阀芯 3Ί和导向球 3'4, 零部件多， 导致轴向尺寸公差累 计较大， 降低了阀的调节精度， 同时装配比较麻烦；
第二， 平衡腔 1'4与第一接口腔 1'2连通， 当第一接口腔 1'2是高压端 时， 平衡腔 Γ4内压强高， 导致密封要求较高， 同时也增大了泄漏的风险； 第三， 在较小的阀芯 3Ί上设置通孔 3Ί1 , 加工比较困难。
有鉴于此， 如何对现有技术中的热力膨胀阀作出改进， 从而一方面能 够提高阀体与阀芯部件上端部之间密封的可靠性， 并提高阀的灵敏度， 且 能够降低阀体与阀芯部件的加工难度； 另一方面能够消除第一接口腔中冷 媒对阀芯部件运动造成的压力影响， 是本领域技术人员亟需解决的问题。 发明内容
本发明要解决的技术问题为提供一种热力膨胀阀， 该热力膨胀阀的结 构设计一方面能够提高阀体与阀芯部件上端部之间密封的可靠性， 并提高 阀的灵敏度， 且能够降低阀体与阀芯部件的加工难度； 另一方面能够消除 第一接口腔中冷媒对阀芯部件运动造成的压力影响。
为解决上述技术问题， 本发明提供一种热力膨胀阀， 包括阀体和阀芯 部件， 所述阀体设有第一接口腔、 内置有传动部件的下腔及隔离二者的第 一密封部件； 所述阀芯部件的侧壁上设有受到所述第一接口腔内冷媒的压 力并受力方向相反的第五承压面和第六承压面； 所述第一密封部件包括设 于所述传动部件与所述阀芯部件上端部之间、 并其第一边缘部密封连接于 所述阀体上的第一柔性密封件； 所述第一柔性密封件的第一承压面的有效 受力面积与所述第五承压面的受力面积之和， 基本等于所述阀芯部件上端 部的第三承压面的有效受力面积与所述第六承压面的受力面积之和。
优选地， 所述第一承压面的有效受力面积基本等于所述第三承压面的 有效受力面积， 所述第五承压面的受力面积基本等于所述第六承压面的受 力面积。
优选地， 所述第五承压面和所述第六承压面均开设于所述第一接口腔 内。
优选地， 所述阔体还设有第二接口腔、 内置有弹性部件的平衡腔及隔 离二者的第二密封部件， 并在所述第二接口腔内所述阀芯部件的侧壁上设 有受力方向相反的第七承压面和第八承压面； 所述第二密封部件包括设于 所述弹性部件与所述阔芯部件下端部之间并其第二边缘部密封连接于所述 阀体上的第二柔性密封件； 所述第二柔性密封件的第二承压面的有效受力 面积与所述第七承压面的受力面积之和， 基本等于所述阀芯部件下端部的 第四承压面的有效受力面积与所述第八承压面的受力面积之和。
优选地， 所述第二承压面的有效受力面积基本等于所述第四承压面的 有效受力面积， 所述第七承压面的受力面积基本等于所述第八承压面的受 力面积。
优选地， 所述阀体设有阀口， 所述阀芯部件设有密封阀口的倾斜密封 面， 所述阀芯部件关闭所述阀口时的密封线或密封面分隔所述倾斜密封面 为处于所述第一接口腔中的所述第六承压面和处于所述第二接口腔中的所 述第七承压面。 优选地， 第一所述柔性密封件为第一波纹管； 所述第一波纹管包括可 沿轴向伸缩的第一波纹套筒部及从一端封闭该第一波纹套筒部的第一直段 部； 所述阔芯部件的上端部伸入所述第一波纹套筒部中， 且其上端面与所 述第一直段部的内侧面贴合。
优选地， 所述传动部件包括传动片及与所述传动片连接的传动釘， 所 述第一直段部设于所述传动釘与所述阀芯部件的上端部之间， 并所述第一 直段部的外侧面与所述传动釘的底壁贴合。
优选地， 所述阔体的顶端部设有安装所述第一柔性密封件的安装孔， 且该安装孔内通过螺纹连接有螺母； 所述螺母通过其内孔套装于所述第一 波纹套筒部和所述传动釘的外部， 并将所述第一边缘部压于所述安装孔的 底壁上； 所述第一边缘部与所述安装孔的底壁之间密封连接。
优选地， 所述第一边缘部的周向末端进一步设有第一翻边， 所述安装 孔侧壁的底端部设有与所述第一翻边位置相对的凹槽； 所述第一翻边伸入 所述凹槽中， 并卡在所述螺母的外侧壁上。
在现有技术的基础上， 本发明所提供的热力膨胀阀的第一密封部件包 括设于所述传动部件与所述阀芯部件上端部之间、 并其第一边缘部密封连 接于所述阀体上的第一柔性密封件； 随着在阀芯部件沿轴向运动， 第一柔 性密封件也随着在轴向上伸缩， 并且其第一边缘部密封连接于阔体上， 因 而该第一密封件始终将所述下腔和所述第一接口腔隔离； 并且具体地， 第 一边缘部和阀体之间的密封方式可以为密封焊接或者采用密封件密封等静 密封结构。 相对于现有技术中的传动密封， 本发明中第一边缘部与阀体之 间的密封是静密封结构， 密封的可靠性高， 泄漏的概率较低， 因而不会加 大热力膨胀阀的过热度， 从而显著提高了热力膨胀阀工作的可靠性和准确 性。 此外， 在本发明中， 密封结构存在于第一边缘部与阀体之间， 而不是 阀芯部件与阀体之间， 因而阀芯部件在沿轴向运动的过程中， 不会受到摩 擦阻力的影响， 因而阀的灵敏度较高。 再者， 在本发明中， 第一边缘部与 阀体之间是静密封结构， 而不是采用现有技术中的传动密封结构， 因而阀 体和阀芯部件的加工精度要求不高， 可以显著降低其加工难度。
此外， 所述第一柔性密封件的第一承压面的有效受力面积与所述第五 承压面的受力面积之和， 基本等于所述阀芯部件上端部的第三承压面的有 效受力面积与所述第六承压面的受力面积之和， 因而可以消除第一接口腔 内冷媒对阀芯部件造成的压力影响。
综上所述， 本发明所提供的热力膨胀阀能够提高阀体与阀芯部件上端 部之间密封的可靠性， 并提高阀的灵敏度， 且能够降低阀体与阀芯部件的 加工难度； 另一方面能够消除第一接口腔中冷媒对阀芯部件运动造成的压 力影响。 附图说明
图 1为现有技术中一种典型的热力膨胀阀的结构示意图；
图 2为本发明一种实施例中热力膨胀阀的结构示意图；
图 3为图 2中热力膨胀阀的 A部位的放大图；
图 4-1为图 2和图 3中第一波纹管在第一种工况下的有效受力面积示 意图；
图 4-2为图 2和图 3中第一波纹管在第二种工况下的有效受力面积示 意图；
图 5为图 2中热力膨胀阀的 B部位的放大图；
图 6为图 2和图 5中第二波纹管的结构示意图；
图 7为图 2中热力膨胀阀的阀芯部件的结构示意图；
图 7-1为图 7中热力膨胀阀的俯视图；
图 7-2为图 7中热力膨胀阀的仰视图；
图 7-3为图 7中热力膨胀阀的 A-A向剖视图；
图 7-4为图 7中热力膨胀阀的 B-B向剖视图；
图 7-5为图 7中热力膨胀阀的 C-C向剖视图。
其中， 图 1中附图标记与部件名称之间的对应关系为：
1'阀体； 1Ί阀口； 1'2第一接口腔； 1'3第二接口腔； 1'4平衡腔；
2Ί膜片； 2'2上腔； 2'3下腔； 2'4气箱座； 2'5气箱盖；
3Ί阀芯; 3Ί1通孔; 3'2传动杆; 3'3传动片; 3'4导向球；
S'l第一承压面； S'2第二承压面； S'3第三承压面； S'4第四承压面； 4Ί毛细管; 4'2感温包; 6'弹簧; 7'导向环;
8Ί第一密封部件； 8'2第二密封部件。
图 2至图 7-5中附图标记与部件名称之间的对应关系为：
1阀体； 11第一接口腔； 12第二接口腔； 13平衡腔； 14安装孔； 141 凹槽； 15螺母； 16第一内台阶面； 17第二内台阶面； 18阀口；
2阀芯部件； 21传动部件； 211传动片； 212传动釘； 22弹性部件；
221弹簧座； 222弹簧； 23密封线；
3气箱； 31气箱座； 32气箱盖； 33膜片； 34上腔； 35下腔；
4第一波纹管； 41第一边缘部； 42第一波纹套筒部； 43第一直段部； 44第一翻边； 45第一密封件；
5第二波纹管； 51第二边缘部； 52第二波纹套筒部； 53第二直段部；
54第二翻边； 55第二密封件；
6调节座； 61第一垫片； 62第二垫片；
S1第一承压面； S2第二承压面； S3第三承压面； S4第四承压面； S5 第五承压面； S6第六承压面； S7第七承压面； S8第八承压面。 具体实施方式
本发明的核心为提供一种热力膨胀阀， 该热力膨胀阀的结构设计一方 面能够提高阀体与阀芯部件上端部之间密封的可靠性，并提高阀的灵敏度， 且能够降低阀体与阀芯部件的加工难度； 另一方面能够消除第一接口腔中 冷媒对阀芯部件运动造成的压力影响。
为了使本领域的技术人员更好地理解本发明的技术方案， 下面结合附 图和具体实施例对本发明作进一步的详细说明。
请参考图 2, 图 3和图 4, 图 2为本发明一种实施例中热力膨胀阀的结 构示意图； 图 3为图 2中热力膨胀阀的 A部位的放大图； 图 4-1为图 2和 图 3中第一波纹管在第一种工况下的有效受力面积示意图； 图 4-2为图 2 和图 3中第一波纹管在第二种工况下的有效受力面积示意图。
在一种实施例中， 如图 2所示， 本发明所提供的热力膨胀阀， 包括阀 体 1及与阀体 1滑动配合的阀芯部件 2, 阀芯部件 2密封阀口 18时， 将阀 体 1的内腔分割为第一接口腔 11和第二接口腔 12; 阀体 1连接有气箱 3 , 气箱 3包括气箱座 31、 气箱盖 32及将气箱 3的内腔分隔为上腔 34和下腔 35的膜片 33 , 气箱 3内进一步设有传动部件 21 ; 所述热力膨胀阀还包括 隔离第一接口腔 11与下腔 35的第一密封部件。
如图 2所示， 在上述现有技术的基础上， 第一密封部件进一步包括可 随阀芯部件 2运动进行伸缩的第一柔性密封件， 所述第一柔性密封件设于 传动部件 21与阀芯部件 2的上端部之间， 且其第一边缘部 41密封连接于 阀体 1上。
随着阀芯部件 2沿轴向运动， 第一柔性密封件也随着在轴向上伸缩， 并且其第一边缘部 41密封连接于阀体 1上，因而该第一柔性密封件始终将 下腔 35和第一接口腔 11隔离； 并且具体地， 第一边缘部 41和阀体 1之间 的密封方式可以为密封焊接或者采用密封件密封等静密封结构。 相对于现 有技术中的传动密封结构，本发明中第一边缘部 41与阀体 1之间的密封是 静密封结构， 密封的可靠性高， 泄漏的概率较低， 因而不会加大热力膨胀 阀的过热度， 从而显著提高了热力膨胀阀工作的可靠性和准确性。 此外， 在本发明中， 密封结构存在于第一边缘部 41与阀体 1之间， 而不是阀芯部 件 2与阀体 1之间， 因而阀芯部件 2在沿轴向运动的过程中， 不会受到摩 擦阻力的影响， 因而阀的灵敏度较高。 再者， 在本发明中， 第一边缘部 41 与阀体 1之间是静密封结构， 而不是采用现有技术中的传动密封结构， 因 而阀体 1和阀芯部件 2的加工精度要求不高， 可以显著降低其加工难度。
此外，所述第一柔性密封件的第一承压面 S1的有效受力面积与第五承 压面 S5的受力面积之和， 基本等于阀芯部件 2上端部的第三承压面 S3的 有效受力面积与第六承压面 S6的受力面积之和，因而可以消除第一接口腔 11内冷媒对阀芯部件 2造成的压力影响。 需要说明的是， 在本文中， 凡涉 及到的 "基本等于或基本相等"， 其内涵为除了包括完全相等的情况外， 还 包括左右偏差正负 5%的的情况。
以下将以第一波纹管 4 为例， 将对第一柔性密封件的第一承压面 S1 的有效受力面积作出解释：
具体地， 设第一接口腔内冷媒压力为 P, 由于第一波纹管 4的位于阀 芯部件 2一侧腔体与第一接口腔 11通过阀芯部件 2与阀体 1之间的间隙连 通， 第一波纹管 4的内部的冷媒压力也为 P; 在此基础上， 分两种工况确 定第一承压面 S1的有效受力面积。 第一种工况为： 如图 4-1所示， 第一边 缘部 41与安装孔 14的底壁仅仅是接触， 但不连接， 因而二者之间不存在 作用力； 在该工况下， 第一波纹管 4内每个波纹均受到相反 ·ί氏消的两个压 力 Ρ, 具体如图 4-1 中箭头所示， 因而第一波纹管的有效受力面积为图 4 中 A S11所示。 第二种工况为： 如图 4-2所示， 第一边缘部 41与安装孔 14 的底壁之间连接固定， 而不仅仅是接触， 因而二者之间存在作用力； 在该 工况下， 由于第一边缘部 41连接固定于安装孔 14的底壁上， 二者之间存 在作用力， 因而第一边缘部 41受到的冷媒压力 Ρ自有所述作用力抵消，对 其不再分析； 第一波纹管其他波纹的受力分析如图 4-2箭头所示， 因而此 时第一承压面 S1的有效受力面积为图 4-2中的 A S12所示。 由此可知， 通 过常规的技术分析，是可以确定第一柔性密封件的第一承压面 S1的有效受 力面积， 并且根据本技术领域内常规的技术手段， 是可以得到第一承压面 S1所需要的有效受力面积。
在上述技术方案的基础上， 可以作出进一步设计， 从而使得结构变得 筒化。 比如，可以使得第一承压面 S1的有效受力面积基本等于第三承压面 S3的有效受力面积，第五承压面 S5的受力面积基本等于第六承压面 S6的 受力面积。
显然， A S11和 A S12相比， A S12更趋近于阀芯部件 2上端面的面积
(在阀芯部件 2上端部的直径一致的情况下，其上端部第三承压面 S3的有 效受力面积等于上端面的面积）， 由此可知， 通过常规的技术设计， 是可以 实现第一承压面 S1的有效受力面积基本等于第三承压面 S3的有效受力面 积。
此外， 在上述技术方案中， 还可以作出进一步改进。 比如， 如图 2所 示， 阀体 1设有阀口 18, 阀芯部件 2设有密封阀口 18的倾斜密封面， 阀 芯部件 2关闭阀口 18时的密封线或密封面分隔所述倾斜密封面为处于第一 接口腔 11中的第六承压面 S6和处于第二接口腔 12中的第七承压面 S7。
在此基础上， 如图 2所示， 平衡腔 13进一步与第一接口腔 11隔离密 封， 且在第一接口腔 11 内阀芯部件 2的侧壁上还开设有与第六承压面 S6 受力方向相反的第五承压面。在本发明中，第五承压面 S5开设于第一接口 腔 11中， 而不是开设于平衡腔 13中， 因而阀芯部件 2上不用开设通孔用 以连通第一接口腔 11和平衡腔 13 , 进而也就避免了使用导向球设于通孔 的下端， 省略了导向球部件， 因而减少了阀芯部件 2的零部件数量， 保证 了其轴向尺寸公差， 提高了阀的调节精度。 此外， 由于不用在阀芯部件 2 上开设通孔， 因而也筒化了阀芯部件 2的加工工艺， 降低了加工难度。 再 者， 由于平衡腔 13进一步与第一接口腔 11隔离密封， 因而当第一接口腔 11是高压端时， 平衡腔 13内始终保持低压， 并且平衡腔 13又同时与第二 接口腔 12隔离密封， 因而平衡腔 13内基本上没有冷媒的存在， 因而显著 降低了平衡腔 13的密封要求。
在上述技术方案的基础上， 还可以作出进一步改进， 从而进一步消除 第二接口腔 12内冷媒压力对阀芯部件 2的压力影响； 具体请参考图 2、 图 5和图 6, 图 5为图 2中热力膨胀阀的 B部位的放大图； 图 6为图 2和图 5 中第二波纹管的结构示意图。
如图 2所示， 阀体 1还设有第二接口腔 12、 内置有弹性部件 22的平 衡腔 13及隔离二者的第二密封部件， 并在第二接口腔 12内阀芯部件 2的 侧壁上设有受力方向相反的第七承压面 S7和第八承压面 S8;在此基础上， 如图 2所示，所述第二密封部件包括设于弹性部件 22与阔芯部件 2下端部 之间、并其第二边缘部 51密封连接于阀体 1上的第二柔性密封件； 该第二 柔性密封件的技术效果与第一柔性密封件的技术效果基本相同， 在此不再 赘述。
此外，由于所述第二柔性密封件的第二承压面 S2的有效受力面积与第 七承压面 S7的受力面积之和， 基本等于阀芯部件 2下端部的第四承压面 S4的有效受力面积与第八承压面 S8的受力面积之和； 因而在上述消除第 一接口腔 11内冷媒对阀芯部件 2造成的压力影响的基础上，进一步消除了 第二接口腔 12内冷媒对阀芯部件 2造成的压力影响，因而无论冷媒由第一 接口腔 11流向第二接口腔 12, 还是由第二接口腔 12流向第一接口腔 11 , 阀芯部件 2受到的系统压差均基本为零， 因而热力膨胀阀可以实现双向平 衡流动。
需要说明的是，对于 "所述第二柔性密封件的第二承压面 S2的有效受 力面积"的解释与上述 "所述第一柔性密封件的第一承压面 S1的有效受力 面积" 解释相同， 在此不再赘述。
进一步地， 为了使得结构筒化， 使得第二承压面 S2、 第四承压面 S4、 第七承压面 S7和第八承压面 S8 易于计算加工， 可以使得第二承压面 S2 的有效受力面积基本等于第四承压面 S4的有效受力面积， 第七承压面 S7 的受力面积基本等于第八承压面 S8的受力面积。
在上述任一种技术方案的基础上， 还可以对第一柔性密封件的具体结 构作出设计。
具体地， 如图 4所示， 该第一柔性密封件具体可以为第一波纹管 4, 该第一波纹管 4包括第一波纹套筒部 42和第一直段部 43 , 第一波纹套筒 部 42可以在轴向上进行伸缩， 第一直段部 43在顶端将第一波纹套筒部 42 的封闭， 使得该第一波套筒部 42的开口朝下； 在此基础上， 如图 3所示， 阀芯部件 2的上端部伸入第一波纹套筒部 42中 ,且其上端面与第一直段部 43的内侧面贴合。 在该结构中， 随着阀芯部件 2沿轴向运动， 第一波纹套 筒部 42在轴向上伸长或压缩，并且伸缩的规律性较高， 因而具有较高的工 作可靠性。 此外， 由于阀芯部件 2上端面与第一直段部 43的内侧面贴合， 因而更有利于力的传递。
在上述技术方案中，如图 2所示，传动部件 21包括传动片 211及与传 动片 211连接的传动釘 212, 第一直段部 43进一步设于传动釘 212与阀芯 部件 2的上端部之间，并第一直段部 43的外侧面与传动釘 212的底壁贴合。 具体地， 为了使得力能够有效传递， 并减少第一直段部 43的异常变形， 如 图 2所示，第一直段部 43与传动釘 212的接触面积应尽可能地大，使得第 一直段部 43的外侧面能够全部或者大体全部覆盖传动釘 212的底壁。
在上述技术方案中，还可以对第一波纹管 4的固定结构作出具体设计。 比如， 如图 2和图 3所示， 阀体 1的顶端部设有安装孔 14, 该安装孔 14 用于设置第一波纹管 4, 同时该安装孔 14内螺纹连接有螺母 15; 具体地， 如图 2和图 3所示， 螺母 15通过其内孔套装于第一波纹套筒部 42和传动 钉 212的外部， 并将第一边缘部 41压于安装孔 14的底壁上； 第一边缘部 41与安装孔 14的底壁之间密封连接。 该种固定结构非常方便地实现了第 一波纹管 4的固定安装， 并且由于螺母 15与安装孔 14之间是可拆卸的螺 纹配合， 因而当第一波纹管 4损坏后， 可以将螺母 15拆卸， 更换第一波纹 管 4。 此外， 螺母 15通过一定的扭矩将第一边缘部 41压于安装孔 14的底 壁上， 因而可以进一步提高第一边缘部 41与安装孔 14的底壁之间的密封 性能。
进一步地， 为了防止第一波纹管 4在径向上发生颤动， 如图 4所示， 第一边缘部 41的周向末端可以进一步设有第一翻边 44, 如图 3所示， 安 装孔 14侧壁的底端部设有与第一翻边 44位置相对的凹槽 141 , 第一翻边 44伸入 EJ槽 141中， 并卡在螺母 15的外侧壁上。
具体地， 还可以对第一边缘部 41与安装孔 14的底壁之间的密封结构 作出设计。 比如， 第一边缘部 41可以密封焊接于安装孔 14的底壁上， 或 者第一边缘部 41与安装孔 14的底壁上可以设有第一密封件 45。
再者， 还可以对第二柔性密封件的具体结构作出设计。
如图 5和图 6所示， 所述第二柔性密封件为第二波纹管 5 , 第二波纹 管 5包括可沿轴向伸缩的第二波纹套筒部 52及在底端封闭该第二波纹套筒 部 52的第二直段部 53; 在此基础上， 如图 6所示， 第二直段部 53夹持于 弹簧座 221与阀芯部件 2的下端部之间。 在该结构中， 随着阀芯部件 2沿 轴向运动，第二波纹套筒部 52在轴向上伸长或压缩， 并且伸缩的规律性较 高， 因而具有较高的工作可靠性。
如图 5所示， 阀芯部件 2的下端部从顶端伸入第二波纹套筒部 52中 , 且其下端面为平面， 并与第一直段部 53的内侧面贴合，从而更有利于力的 传递； 此外， 第二直段部 53的外侧面与弹簧座 221的顶壁贴合； 具体地， 如图 5所示，弹簧座 221的顶端设有槽体，该第二直段部 53设于该槽体中； 在此基础上， 为了使得力更有效地传递，并避免第二直段部 53发生异常变 形， 第二直段部 53应与槽体的底壁接触面积最大化， 使得第二直段部 53 的外侧面全部或大体全部覆盖槽体的底壁。
具体地，还可以对第二边缘部 51与阀体 1之间的固定结构作出具体设 计。 比如， 如图和图 5所示， 阀体 1的下端配合有调节座 6, 阀体 1设有 内台阶面，具体地，调节座 6通过螺纹配合设于阀体 1下端的内螺纹孔中； 在此基础上， 第二边缘部 51夹持于调节座 6的顶壁与所述内台阶面之间， 并第二边缘部 51与所述内台阶面密封连接。该种结构设计非常方便地实现 了第二边缘部 51的固定， 并且结构比较筒单， 成本较低。
当然， 还可以上述固定结构作出进一步改进。 比如， 如图 5和图 6所 示， 调节座 6的顶壁与所述内台阶面之间进一步沿轴向排列设有第一垫片 61和第二垫片 62,所述内台阶面包括第一内台阶面 16和第二内台阶面 17, 第一垫片 61支撑于第一内台阶面 16上，第二垫片 62支撑于第二内台阶面 17上； 在此基础上， 第二边缘部 51进一步夹持于第一垫片 61与第二垫片 62之间， 并第二边缘部 51与第一内台阶面 16密封连接。 该种结构设计通 过两个垫片夹持固定的方式将第二边缘部 51的位置固定，从而避免第二边 缘部 51 由于受到冷媒的挤压而对其与阀体 1之间的密封连接结构造成破 坏， 提高了工作的稳定性和可靠性。
进一步地， 如图 5所示， 第一垫片 61 以其内孔设于第二波纹套筒部
52的外部；第二垫片 62的内端部沿径向向内侧超出第一垫片 61的内端部， 并与第二边缘部 51的内端部贴合。 该种结构设计使得第二垫片 62大体全 部覆盖第二边缘部 51 , 使得第二波纹套筒部 52的伸缩更具有规律性， 避 免第二波纹套筒部在 52伸缩过程中发生较大变形， 进而提高工作的可靠 性。
此外， 为了防止第二波纹管 5在径向上发生颤动， 如图 5所示， 第二 边缘部 51 的周向末端进一步设有卡在第一垫片 61 外侧壁上的第二翻边 55。
再者， 需要说明的是， 第一波纹管 4和第二波纹管 5的刚度可以进一 步相等， 并且第一波紋管 4和第二波紋管 5反向设置， 因而第一波紋管 4 和第二波纹管 5对阀芯部件 2的作用弹力相等， 并方向相反， 因而不会对 阀芯部件 2带来额外的附加力。
以下将对第三承压面至第八承压面作出具体说明， 具体请参见图 7、 图 7-1、 图 7-2、 图 7-3、 图 7-4和图 7-5 , 图 7为图 2中热力膨胀阀的阀芯 部件的结构示意图； 图 7-1为图 7中热力膨胀阀的俯视图； 图 7-2为图 7 中热力膨胀阀的仰视图； 图 7-3为图 7中热力膨胀阀的 A-A向剖视图； 图 7-4为图 7中热力膨胀阀的 B-B向剖视图； 图 7-5为图 7中热力膨胀阀的 C-C向剖视图。
如图 7-1所示， 第三承压面 S3的受力面积为 A S3; 如图 7-2所示， 第 四 压面 S4的受力面积为 A S4; 如图 7-3所示， 第五 压面 S5的受力面 积为 A S5; 如图 7-4所示， 第六承压面 S6的受力面积为 A S6, 第七承压面 S7的受力面积为 A S7; 如图 7-5所示， 第八 压面 S8的受力面积为 A S8。
以上对本发明所提供的热力膨胀阀进行了详细介绍。 本文中应用了具 于帮助理解本发明的方法及其核心思想。 应当指出， 对于本技术领域的普 通技术人员来说， 在不脱离本发明原理的前提下， 还可以对本发明进行若 干改进和修饰， 这些改进和修饰也落入本发明权利要求的保护范围内。

Claims

权 利 要 求
1、 一种热力膨胀阀， 包括阀体（1)和阀芯部件 （2), 所述阀体（1) 设有第一接口腔（11)、 内置有传动部件（21)的下腔（35)及隔离二者的 第一密封部件； 所述阀芯部件（ 2 )的侧壁上设有受到所述第一接口腔（ 11 ) 内的冷媒压力并受力方向相反的第五承压面 （S5)和第六承压面 （S6); 其特征在于， 所述第一密封部件包括设于所述传动部件 （21 )与所述阀芯 部件（2)上端部之间、 并其第一边缘部 （41) 密封连接于所述阀体（1) 上的第一柔性密封件； 所述第一柔性密封件的第一承压面 （S1) 的有效受 力面积与所述第五承压面 （S5) 的受力面积之和， 基本等于所述阀芯部件 (2)上端部的第三承压面 （S3) 的有效受力面积与所述第六承压面 （S6) 的受力面积之和。
2、如权利要求 1所述的热力膨胀阀，其特征在于，所述第一承压面（S1 ) 的有效受力面积基本等于所述第三承压面 （S3) 的有效受力面积， 所述第 五承压面 （S5) 的受力面积基本等于所述第六承压面 （S6) 的受力面积。
3、如权利要求 1所述的热力膨胀阀，其特征在于，所述第五承压面（S5) 和所述第六承压面 （S6) 均开设于所述第一接口腔（11) 内。
4、 如权利要求 1至 3任一项所述的热力膨胀阀， 其特征在于， 所述阀 体（1 )还设有第二接口腔（12)、 内置有弹性部件 （22) 的平衡腔（13) 及隔离二者的第二密封部件， 并在所述第二接口腔（12) 内所述阀芯部件 (2)的侧壁上设有受力方向相反的第七承压面（S7)和第八承压面（S8); 所述第二密封部件包括设于所述弹性部件（22)与所述阔芯部件（2)下端 部之间、 并其第二边缘部（52)密封连接于所述阀体（ 1 )上的第二柔性密 封件； 所述第二柔性密封件的第二承压面 （S2) 的有效受力面积与所述第 七承压面（S7)的受力面积之和， 基本等于所述阀芯部件（2)下端部的第 四承压面（ S4 )的有效受力面积与所述第八承压面（ S8 )的受力面积之和。
5、如权利要求 4所述的热力膨胀阀，其特征在于，所述第二承压面（ S2 ) 的有效受力面积基本等于所述第四承压面 （S4) 的有效受力面积， 所述第 七承压面 （S7) 的受力面积基本等于所述第八承压面 （S8) 的受力面积。
6、 如权利要求 4所述的热力膨胀阀， 其特征在于， 所述阀体（1)设 有阀口 （18), 所述阀芯部件（2)设有密封阀口 （18) 的倾斜密封面， 所 述阀芯部件（2)关闭所述阀口 （18)时的密封线（23)或密封面分隔所述 倾斜密封面为处于所述第一接口腔（11 ) 中的所述第六承压面 （S6)和处 于所述第二接口腔（12) 中的所述第七承压面 （S7)。
7、 如权利要求 1至 6任一项所述的热力膨胀阀， 其特征在于， 第一所 述柔性密封件为第一波纹管（4); 所述第一波纹管（4)包括可沿轴向伸缩 的第一波纹套筒部 （42) 及从一端封闭该第一波纹套筒部 （42) 的第一直 段部 （43); 所述阀芯部件 （2) 的上端部伸入所述第一波纹套筒部 （42) 中， 且其上端面与所述第一直段部 （43) 的内侧面贴合。
8、如权利要求 7所述的热力膨胀阀，其特征在于，所述传动部件（ 21 ) 包括传动片 （211 )及与所述传动片 （211)连接的传动釘（212), 所述第 一直段部 （43)设于所述传动釘（212) 与所述阀芯部件 （2) 的上端部之 间， 并所述第一直段部 （43) 的外侧面与所述传动釘（212) 的底壁贴合。
9、 如权利要求 8所述的热力膨胀阀， 其特征在于， 所述阀体（1) 的 顶端部设有安装所述第一波纹管 （4) 的安装孔（14), 且该安装孔（14) 内通过螺纹连接有螺母（ 15 ); 所述螺母（ 15 )通过其内孔套装于所述第一 波纹套筒部（ 42 )和所述传动釘（ 212 )的外部， 并将所述第一边缘部（ 41 ) 压于所述安装孔（ 14 )的底壁上；所述第一边缘部（ 41 )与所述安装孔（ 14 ) 的底壁之间密封连接。
10、 如权利要求 9所述的热力膨胀阀， 其特征在于， 所述第一边缘部
(41)的周向末端进一步设有第一翻边（45), 所述安装孔（14)侧壁的底 端部设有与所述第一翻边（ 45 )位置相对的凹槽（ 141 );所述第一翻边（ 45 ) 伸入所述凹槽（141) 中， 并卡在所述螺母（15) 的外侧壁上。
PCT/CN2012/074790 2011-04-27 2012-04-27 热力膨胀阀 WO2012146193A1 (zh)

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