WO2022143289A1 - 一种电动阀 - Google Patents

一种电动阀 Download PDF

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Publication number
WO2022143289A1
WO2022143289A1 PCT/CN2021/139971 CN2021139971W WO2022143289A1 WO 2022143289 A1 WO2022143289 A1 WO 2022143289A1 CN 2021139971 W CN2021139971 W CN 2021139971W WO 2022143289 A1 WO2022143289 A1 WO 2022143289A1
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WO
WIPO (PCT)
Prior art keywords
planetary gear
stage planetary
ring gear
rotor
electric valve
Prior art date
Application number
PCT/CN2021/139971
Other languages
English (en)
French (fr)
Inventor
徐铭辉
吴翰麒
Original Assignee
浙江三花制冷集团有限公司
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 浙江三花制冷集团有限公司 filed Critical 浙江三花制冷集团有限公司
Priority to KR1020237017441A priority Critical patent/KR20230090360A/ko
Priority to JP2023546381A priority patent/JP2023544654A/ja
Priority to US18/034,131 priority patent/US20230392711A1/en
Publication of WO2022143289A1 publication Critical patent/WO2022143289A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/0647—Spindles or actuating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/53—Mechanical actuating means with toothed gearing
    • F16K31/535—Mechanical actuating means with toothed gearing for rotating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
    • F16K31/043—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H2001/327—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear with orbital gear sets comprising an internally toothed ring gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing

Definitions

  • the invention relates to the technical field of fluid control, in particular to an electric valve.
  • FIG. 1 is a partial cross-sectional schematic diagram of an electric valve given in the background art.
  • the electric valve includes a housing part 01, a rotor part 02, a gear assembly 03 and a transmission rod 04.
  • the rotor part 02 and the gear assembly 03 are located in the inner cavity of the housing part 01, and the gear assembly 03 includes a ring gear 031, a sun gear part 032, planetary gear set 033 and output gear set 034.
  • the action process is as follows: the rotation of the rotor part 02 drives the sun gear part 032 to rotate.
  • the rotation of the sun gear member 032 drives the planetary gear set 033 to rotate, the rotation of the planetary gear set 033 drives the output gear set 034 to rotate, and the output gear set 034 drives the transmission rod 04 to rotate.
  • the electric valve of this structure converts the small torque output by the rotor part 02 into a larger output torque through the gear assembly 03, so as to drive the transmission rod 04 to rotate to realize the function of the electric valve. How to optimize the structure of the electric valve to realize the miniaturization of the electric valve is a problem that needs to be considered by those skilled in the art.
  • the object of the present invention is to provide an electric valve, including a control part, a valve body part and a gear reduction mechanism, the control part includes a rotor part, the valve body part includes a transmission rod, and the gear reduction mechanism includes a first ring gear , a second ring gear, an upper planetary gear assembly and a lower planetary gear assembly arranged along the longitudinal direction of the electric valve, at least part of the first ring gear is located in the inner cavity of the rotor part, and the rotor part includes an input gear part , the input gear portion meshes with the planetary gears of the upper planetary gear assembly, the planetary gears of the upper planetary gear assembly mesh with the first ring gear, and the planetary gears of the lower planetary gear assembly mesh with the second The ring gear is engaged, and the lower planetary gear assembly is rotatably connected with the transmission rod.
  • the gear reduction mechanism includes a first ring gear, a second ring gear, an upper planetary gear assembly and a lower planetary gear assembly arranged in the longitudinal direction of the electric valve, and at least part of the first ring gear is located inside the rotor part.
  • the input gear part of the rotor part meshes with the planetary gears of the upper planetary gear assembly, and the lower planetary gear assembly is rotatably connected with the transmission rod.
  • at least part of the first ring gear is located in the inner cavity of the rotor part, which is beneficial to reduce the volume of the electric valve.
  • Fig. 1 the sectional schematic diagram of a kind of electric valve given in the background art
  • Figure 2 a schematic cross-sectional view of an electric valve provided by the present invention
  • Fig. 3 The partial enlarged schematic diagram of Fig. 2;
  • Figure 4 A schematic structural diagram of the second ring gear in Figure 2;
  • Figure 5a a half-section perspective view of the first ring gear in Figure 2;
  • Figure 5b a schematic structural diagram of the first ring gear in Figure 5a;
  • Figure 6a perspective view 1 of the output gear carrier in Figure 2;
  • Figure 6b perspective view 2 of the output gear carrier in Figure 2;
  • Figure 7 a schematic structural diagram of the second housing part in Figure 2;
  • Figure 8 The schematic diagram of the cooperation of the second housing part, the first ring gear and the output gear carrier in Figure 2;
  • Figure 9 a cross-sectional view of another first ring gear provided by the present invention.
  • Figure 10 A schematic diagram of the structure of the first ring gear in Figure 9;
  • FIG. 11 is a schematic structural diagram of another output gear carrier provided by the present invention.
  • circumferential rotation refers to the movement in the circumferential direction, including not only the movement of more than one rotation (360°), but also the movement within one rotation (360°).
  • Fig. 2 is a schematic sectional view of an electric valve provided by the present invention
  • Fig. 3 is a partial enlarged schematic view of Fig. 2
  • Fig. 4 is a schematic structural diagram of the first ring gear in Fig. 2
  • Half-section perspective view
  • Figure 5b is a schematic structural diagram of the second ring gear in Figure 5a
  • Figure 6a is a perspective view of the output gear rack in Figure 2
  • Figure 6b is a perspective view of the output gear rack in Figure 2
  • FIG. 8 is a schematic diagram of the cooperation of the second housing part, the second ring gear and the output gear frame in FIG. 2 .
  • the electric valve includes a control part 1 , a gear reduction mechanism 2 , a housing part 3 , and a valve body part 4 .
  • the valve cavity of the electric valve includes the inner cavity 30 of the housing part and the inner cavity 40 of the valve body part.
  • the valve body part 4 includes a transmission rod 41 , a valve core 42 and a valve body 43 .
  • the control part 1 includes a coil 11 , a rotor part 12 , a bearing part 13 , a spring 14 , a positioning seat 15 and a positioning rod 16 .
  • the coil 11 is located outside the housing part 3, and the rotor part 12, the bearing part 13, the spring 14, the positioning seat 15 and the positioning rod 16 are located in the inner cavity 30 of the housing part.
  • the coil 11 is energized to drive the rotor member 12 to rotate in the circumferential direction.
  • the positioning seat 15 is located above the rotor component 12, the upper end of the positioning rod 16 is located in the first blind hole 151 of the positioning seat 15, and the lower end of the positioning rod 16 is located in the second blind hole 410 of the transmission rod 41, so as to realize the positioning rod 16. position.
  • the positioning rod 16 penetrates through the bearing member 13 , the rotor member 12 , and the first-stage planetary gear carrier 231 , the second-stage planetary gear carrier 241 , and the third-stage planetary gear carrier 251 of the gear reduction mechanism 2 .
  • the positioning of the positioning rod 16 can ensure The coaxiality of the rotor component 12 and the gear reduction mechanism 2 improves the transmission reliability between the rotor component 12 and the gear reduction mechanism 2 . At the same time, it is also beneficial to improve the action stability of the gear reduction mechanism 2 and reduce the risk of jamming.
  • the rotor part 12 has a through hole 120 , the positioning rod 16 penetrates through the through hole 120 , and the positioning rod 16 is in clearance fit with the hole wall 1201 forming the through hole 120 .
  • the rotor part 12 includes a bracket 121 and a rotor 122 fixedly connected to the bracket 121 .
  • the rotor 122 is made by magnetic powder sintering.
  • the bracket 121 is fixedly connected to the rotor 122 by injection molding.
  • the bracket 121 has the aforementioned through hole 120.
  • the bracket 121 includes a shaft portion 123.
  • the bearing member 13 is located between the positioning seat 15 and the bracket 121 , the spring 14 is partially sheathed on the positioning seat 15 , and the other part of the spring 14 is sheathed on the bearing member 13 , one end of the spring 14 abuts on the positioning seat 15 , and the other end of the spring 14 abuts on the bearing The bearing member 13 abuts the bracket 121 .
  • the gear reduction mechanism 2 is provided in the inner cavity 30 of the housing member.
  • the gear reduction mechanism 2 includes a first ring gear 21 , a second ring gear 22 , an upper planetary gear assembly 201 and a lower planetary gear assembly 202
  • the upper planetary gear assembly 201 includes a first-stage planetary gear set 23 and a second-stage planetary gear set 24
  • the lower planetary gear assembly 202 includes a third-stage planetary gear set 25 and a fourth-stage planetary gear set 26 .
  • the first-stage planetary gear set 23 , the second-stage planetary gear set 24 , the third-stage planetary gear set 25 and the fourth-stage planetary gear set 26 are sequentially arranged along the longitudinal direction of the electric valve.
  • the first-stage planetary gear set 23 is located in the inner cavity 210 of the first ring gear, and includes a first-stage planetary gear carrier 231 and a first-stage planetary gear 232 mounted on the first-stage planetary gear carrier 231.
  • the aforementioned input gear The second-stage planetary gear set 24 includes a second-stage planetary gear carrier 241 and a second-stage planetary gear 242 mounted on the second-stage planetary gear carrier 241.
  • the second-stage planetary gear Part of the carrier 241 is located in the inner cavity 210 of the first ring gear, and the other part is located in the inner cavity 220 of the second ring gear.
  • the second stage planetary gear 242 is located in the inner cavity 210 of the first ring gear.
  • the gears mesh with the second stage planetary gears 242 .
  • the planetary gears of the upper planetary gear assembly 201 include a first-stage planetary gear 232 and a second-stage planetary gear 242 , and the first-stage planetary gear 232 and the second-stage planetary gear 242 have the same module. It should be noted that, when the number of teeth of the planetary gear is constant, the larger the module, the larger the radial dimension of the gear.
  • the third-stage planetary gear set 25 and the fourth-stage planetary gear set 26 are located in the inner cavity 220 of the second ring gear.
  • the third-stage planetary gear set 25 includes a third-stage planetary gear carrier 251 and a third-stage planetary gear 252 mounted on the third-stage planetary gear carrier 251 , the sun gear and the third-stage planetary gear of the second-stage planetary gear carrier 241 252 meshes;
  • the fourth-stage planetary gear set 26 includes an output gear carrier 261 and a fourth-stage planetary gear 262 mounted on a column 263 of the output gear carrier 261 , the sun gear of the third-stage planetary gear carrier 251 and the fourth-stage planetary gear 262 mesh.
  • the planetary gears of the lower planetary gear assembly 202 include a third-stage planetary gear 252 and a fourth-stage planetary gear 262, and the third-stage planetary gear 252 and the fourth-stage planetary gear 262 have the same module.
  • the modulus of the planetary gears of the upper planetary gear assembly 201 is smaller than that of the planetary gears of the lower planetary gear assembly 202 , that is, the modulus of the second-stage planetary gears 242 is smaller than that of the third-stage planetary gears 252 .
  • the input gear portion 1211 of the rotor member 12 meshes with the first-stage planetary gears 232 of the upper planetary gear assembly 201 , and the first-stage planetary gears 232 in turn transmit torque to the second-stage through the first-stage planetary gear carrier 231
  • the planetary gear 242 because the planetary gear of the upper planetary gear assembly 201 is close to the rotor part 12 (torque input end), bears a small load and requires low strength, so a planetary gear with a small modulus (small size) can be used; the lower planetary gear
  • the planetary gear of the assembly 202 is close to the transmission rod 41 (torque output end), and bears a large load and requires high strength.
  • a planetary gear with a large module needs to be used.
  • setting the module of the planetary gear of the upper planetary gear assembly to be smaller than the module of the planetary gear of the lower planetary gear assembly is beneficial to reduce the size of the planetary gear of the upper planetary gear assembly and the lateral size of the electric valve. Thereby reducing the volume of the electric valve.
  • the output gear rack 261 includes a central hole 2610 , the cross-sectional profile of the central hole 2610 is non-circular, and the upper end of the transmission rod 41 extends into the central hole 2610 to realize the rotational connection with the output gear rack 261 , and the output gear rack 261 can drive the transmission rod 41 turn.
  • the transmission rod 41 is rotatably connected with the valve core 42, and the transmission rod 41 can drive the valve core 42 to rotate to realize the valve opening, closing or flow regulating function of the electric valve.
  • the inner wall of the first ring gear 21 is provided with first inner teeth 214 extending along the longitudinal direction of the first ring gear 21 , and both the first-stage planetary gears 232 and the second-stage planetary gears 242 pass through the first inner teeth 214 It meshes with the first ring gear 21 .
  • the inner wall of the second ring gear 22 is provided with axially extending second inner teeth 2211 .
  • the first-stage planetary gear carrier 231 , the first-stage planetary gear 232 , the second-stage planetary gear carrier 241 , and the second-stage planetary gear 242 can be made of plastic, and specifically, are injection-molded from materials such as nylon, PPS, and PEEK.
  • the housing part 3 includes a first housing part 31 , a second housing part 32 and a coil mounting frame 33 .
  • the first housing part 31 and the second housing part 32 are respectively made of stainless steel plate or pipe.
  • the housing part 31 and the second housing part 32 are fixed by welding, the first housing part 31 and the coil mounting frame 33 are fixed by welding, and the second housing part 32 and the valve body 43 are fixed by welding.
  • the rotor part 12 is located in the inner cavity 310 of the first housing part, and the coil 11 is sheathed in the first housing part 31 and fixed to the coil mounting frame 33 .
  • the first housing part 31 includes an equal diameter section 311 and an enlarged diameter section 312 . As shown in FIG.
  • the wall thickness of the equal diameter section 311 is smaller than that of the second housing part 32 , and the rotor component 12 is located in the equal diameter section 311 , the aforementioned coil 11 is covered with an equal diameter section 311 .
  • the upper section of the second housing portion 32 is provided with an outer stepped portion 321 , the enlarged diameter section 312 is placed on the outer stepped portion 321 , and the lower end of the enlarged diameter section 312 is fixed to the outer stepped portion 321 by welding.
  • the beneficial effect of disposing the outer step portion 321 is that the first shell portion 31 and the second shell portion 32 can be easily positioned during welding, and the welding quality can be improved.
  • the wall thickness of the equal diameter section 311 is smaller than the wall thickness of the second housing part 32, and the beneficial effect is that setting the wall thickness of the equal diameter section 311 to be thinner is conducive to increasing the magnetic flux, improving the driving efficiency of the coil 11, and reducing energy consumption;
  • a thicker wall thickness of the second housing portion 32 is beneficial to increase the compressive strength and improve the service life, and is not easily damaged even if it is subjected to a strong impact force of the refrigerant.
  • the lower section of the second housing portion 32 includes a diameter-reduced portion 322
  • the diameter-reduced portion 322 is cylindrical
  • the valve body 43 of the valve body part 4 includes a protrusion protruding toward the direction of the control part 1 .
  • the protruding portion 431 and the protruding portion 431 are cylindrical
  • the diameter reducing portion 322 is at least partially located in the inner cavity of the protruding portion 431
  • the diameter reducing portion 322 and the protruding portion 431 are welded and fixed. It is conceivable that the protruding portion 431 may also be at least partially located in the inner cavity of the reduced diameter portion 322 .
  • the first ring gear 21 is roughly cylindrical, and the first ring gear 21 is made of plastic, specifically nylon, PPS, PEEK and other materials Injection molding.
  • the first ring gear 21 is located in the inner cavity 310 of the first housing part 31 , while the first ring gear 21 is at least partially located in the inner cavity of the rotor part 12 , and the first ring gear 21 is placed above the second ring gear 22 .
  • the first ring gear 21 includes a supporting portion 211 , a positioning portion 212 and a clamping portion 213 .
  • the supporting portion 211 is located above the positioning portion 212 , the positioning portion 212 is located above the clamping portion 213 , and the outer diameter of the positioning portion 212 is larger than the outer diameter of the supporting portion 211 .
  • the outer diameter of the clamping portion 213 is larger than the outer diameter of the positioning portion 212 .
  • the support portion 211 is at least partially located in the inner cavity 1220 of the rotor 122 , and the positioning portion 212 is located below the rotor 122 . Extending at least part of the support portion 211 into the inner cavity 1220 of the rotor 122 can reduce the axial dimension of the electric valve, which is beneficial to reduce the volume of the electric valve and realize miniaturization.
  • the support portion 211 includes a through hole 2110, and the support portion 211 supports the rotor member 12 in the longitudinal direction of the electric valve.
  • the shaft portion 123 of the bracket 121 penetrates through the through hole 2110 of the support portion and extends into the inner cavity 210 of the first ring gear 21 .
  • the shaft portion 123 includes an input gear portion 1211 , which is located in the inner cavity 210 of the first ring gear 21 and Meshing with the first-stage planetary gear 232 , the shaft portion 123 is in clearance fit with the hole wall 2111 of the support portion 211 that forms the through hole 2110 . This arrangement improves the reliability of transmission between the rotor component 12 and the gear reduction mechanism 2 .
  • the bracket 121 includes a lower stepped portion 1212 with a stepped surface facing downward, the input gear portion 1211 is located below the lower stepped portion 1212 , the stepped surface 1214 of the lower stepped portion 1212 is in contact with the upper end surface 2112 of the support portion 211 , and the lower stepped portion
  • the stepped wall 1213 of 1212 is in clearance fit with the hole wall 2111 forming the through hole 2110 , and the support portion 211 cooperates with the lower stepped portion 1212 to rotatably support the bracket 121 , that is, the rotor component 12 can rotate relative to the first ring gear 21 in the circumferential direction.
  • the outer wall of the positioning portion 212 is in clearance fit with the inner wall of the equal diameter section 311 of the first housing portion 31 .
  • the "clearance fit” here refers to a fit with a clearance (including the minimum clearance equal to zero).
  • the clearance between the outer peripheral wall of the positioning portion 212 and the inner wall of the equal diameter section 311 of the first housing portion 31 0 ⁇ g ⁇ 0.2mm.
  • the positioning portion 212 is a plurality of ribs extending along the axial direction of the first ring gear 21 , and grooves are formed between adjacent ribs, so that the material can be saved and the weight of the first ring gear 21 can be reduced.
  • the latching portion 213 includes a first concave portion 2131
  • the second ring gear 22 includes a first convex portion 2212 protruding toward the direction of the control member 1
  • the first convex portion 2212 is located at the upper end of the second gear ring 22
  • the portion 2212 and the first concave portion 2131 are concave-convex matched to limit the circumferential rotation of the first ring gear 21 , that is, the first ring gear 21 and the second ring gear 22 are connected in a limited circumferential direction.
  • the snap portion 213 may be provided with a convex portion
  • the second ring gear 22 may be provided with a concave portion
  • the circumferential limit can also be achieved through the concave-convex fit.
  • the first ring gear 21 and the second ring gear 22 may also be fixedly connected by welding.
  • an elastic member 5 is also included.
  • the elastic member 5 is arranged between the enlarged diameter section 312 of the first housing portion 31 and the clamping portion 213 , and elastically abuts against the inner wall of the enlarged diameter section 312 . and the upper end surface of the engaging portion 213 to prevent the first ring gear 21 and the second ring gear 22 from moving axially.
  • the elastic member 5 here may be an elastic ring made of non-metallic materials such as rubber as shown in FIG. 2 , or may be a metal elastic sheet made of a metal material.
  • the first ring gear 21 is radially limited by the positioning rod 16, and the second ring gear 22 is circumferentially limited by the second housing part 32 (in this embodiment, the second housing part 32 and the second ring gear 22
  • the concave-convex fit is used to realize the circumferential limit, which will be described in detail later).
  • the positioning of the first ring gear 21 and the second ring gear 22 can be achieved without welding, and the components are easily assembled in this way, and no welding is required.
  • the second ring gear 22 has an integral structure, is roughly cylindrical in shape with a large upper and a small lower, and is made of metal powder metallurgy.
  • the second ring gear 22 includes a large diameter section 221 and a small diameter section 222 .
  • the aforementioned second inner teeth 2211 are provided on the inner peripheral wall of the large diameter section 221
  • the aforementioned first protrusions 2212 are provided on the upper end of the large diameter section 221 .
  • the large-diameter section 221 includes a second protruding portion 2213 , and the second protruding portion 2213 protrudes radially outward from the outer peripheral wall of the large-diameter section 221 .
  • the stepped wall 3211 of the outer stepped portion 321 of the second housing portion 32 includes a second concave portion 3210 , and the second convex portion 2213 and the second concave portion 3210 are concave and convex to restrict the circumferential rotation of the second ring gear 22 .
  • the second ring gear 22 is made of metal powder metallurgy, the second inner teeth 2211, the first protruding portion 2212 and the second protruding portion 2213 are integrally formed during manufacture, which is convenient for processing.
  • 32 is made of metal plate or pipe by drawing, and the second recess 3210 only needs to be machined, which is convenient to process.
  • the second ring gear 22 and the second housing part 32 are positioned through concave-convex fitting, and the assembly is simple.
  • the second ring gear 22 may be provided with a concave portion, and the second housing portion 32 may be provided with a convex portion, and the circumferential position limit can also be achieved through the concave-convex fit.
  • the second ring gear 22 and the second housing portion 32 may also be fixedly connected by welding.
  • the small diameter section 222 is at least partially located in the inner cavity of the reduced diameter portion 322 of the second housing portion 32 .
  • the second ring gear 22 includes a through hole 2201 extending in the longitudinal direction of the electric valve.
  • the transmission rod 41 penetrates through the through hole 2201 and is in clearance fit with the hole wall forming the through hole 2201 .
  • the transmission rod 41 can rotate relative to the second ring gear 22 .
  • the upper end of the transmission rod 41 is located in the inner cavity 30 of the housing part, and the lower end of the transmission rod 41 is located in the inner cavity 40 of the valve body part.
  • the beneficial effect is that the second ring gear 32 is made of self-lubricating metal material powder metallurgy, so that the frictional resistance of the transmission rod 41 is small when it rotates, and the wear of the transmission shaft 41 during the rotation process can be reduced, and its service life can be improved.
  • the second ring gear 32 integrates the function of a bearing, so there is no need to provide a separate bearing, which reduces the number of parts and components.
  • the second ring gear 22 further includes a transition section 223, the transition section 223 is located between the large diameter section 221 and the small diameter section 222, and the output gear carrier 261 is placed on the Above the transition section 223 , the through hole 2201 of the second ring gear 22 includes an inner hole 2220 of the small diameter section 222 and an inner hole 2230 of the transition section 223 .
  • the second ring gear 22 further includes a limiting protrusion 2231 , and the limiting protrusion 2231 protrudes from the transition section 223 toward the control member 1 . Further, the limiting protrusion 2231 is connected to the inner peripheral wall of the large diameter section 221 , and the limiting protrusion 2231 is integrally formed with the second ring gear 22 during metal powder metallurgy.
  • the side of the output gear frame 261 facing the valve body part 4 includes a limit groove 264 , the limit protrusion 2231 is at least partially located in the limit groove 264 , and the limit protrusion 2231 can be connected with the two grooves of the limit groove 264
  • the wall 266 abuts to limit the rotation stroke of the output gear frame 261 , that is, the rotation stroke of the transmission shaft 41 .
  • This setting can limit the rotation stroke of the valve core 42 and realize the fully open, fully closed and flow regulating functions of the electric valve.
  • the valve core of the electric valve in this embodiment adopts a spherical valve core.
  • valve core angle of the electric valve in the fully closed state is defined as 0°
  • the limit is The two groove walls 266 of the bit groove 264 limit the maximum rotation of the output gear carrier 261 to 90°.
  • the valve core 42 has a substantially spherical shape, but it may not be limited to a spherical shape, such as a hemispherical shape or a spindle shape.
  • the number of the above-mentioned limiting protrusions 2231 is set to two, and is symmetrically arranged with respect to the central axis of the through hole 2220 of the small diameter section 222.
  • the side of the output gear carrier 261 facing the valve body part 4 further includes a third raised portion 265 , the lower end of the third raised portion 265 is substantially arc-shaped or platform-shaped, and the third raised portion 265 abuts against the transition section 223.
  • the third protrusions 265 By arranging the third protrusions 265, the contact area between the output gear carrier 261 and the transition section 223 can be reduced, so that the wear of the output gear carrier 261 can be reduced and the service life thereof can be improved.
  • the transmission rod 41 includes a flange portion 411 , the flange portion 411 is located below the small diameter section 222 of the second ring gear 22 , and the flange portion 411 can abut against the lower end of the small diameter section 222 to restrict the transmission rod 41
  • the axial upward movement can prevent the transmission rod 41 from tilting the output gear frame 261 , which affects the reliable transmission of the reduction gear mechanism 2 .
  • the second ring gear 22 includes a communication channel 200, and the communication channel 200 communicates with the inner cavity 220 of the second ring gear 22 and the inner cavity 40 of the valve body part.
  • the communication channel 200 includes a communication hole 2230 and a side groove 2221.
  • the communication hole 2230 communicates with the side groove 2221.
  • the communication hole 2230 is provided in the transition section 223.
  • the communication hole 2230 penetrates the transition section 223.
  • the side grooves 2221 extend in the longitudinal direction of the second ring gear 22 .
  • FIG. 9 is a cross-sectional view of another second ring gear provided by the present invention
  • FIG. 10 is a schematic structural diagram of the second ring gear in FIG. 9
  • FIG. 11 is a structural schematic diagram of another output gear carrier provided by the present invention.
  • the difference between this embodiment and the above-mentioned embodiment mainly lies in the matching structure of the second ring gear and the output gear carrier.
  • the second ring gear 22A includes a transition section 223A on which the output carrier 261A is positioned.
  • the transition section 223A includes an arc-shaped hole 2232A.
  • the arc-shaped hole 2232A is a circular arc-shaped through hole, of course, it can also be a circular arc-shaped blind hole.
  • the side of the output gear carrier 261A facing the valve body part 4 includes a limiting boss 266A, the limiting boss 266A is at least partially located in the arc-shaped hole 2232A, and the limiting boss 266A can be connected with the two ends forming the arc-shaped hole 2232A.
  • the wall 2233A abuts to limit the rotation stroke of the output gear frame 261A, that is, the rotation stroke of the transmission shaft 41.
  • This setting can limit the rotation stroke of the valve core 42 and realize the fully open, fully closed and flow regulating functions of the electric valve.
  • the valve core of the electric valve in this embodiment adopts a spherical valve core. If the valve core angle of the electric valve in the fully closed state is defined as 0°, when the valve core rotates 90° to reach the fully open state, that is, the arc
  • the two end walls 2233A of the shaped hole 2232A define a maximum rotational travel of the output carrier 261A of 90°.
  • the difference between the present embodiment and the above-mentioned embodiment is the arrangement of the communication channel of the second ring gear.
  • the second ring gear 22A includes a communication channel 200A, and the communication channel 200A communicates with the inner cavity 220 of the second ring gear and the inner cavity 40 of the valve body part.
  • the communication channel 200A includes an arc-shaped hole 2232A and the aforementioned side groove 2221 .
  • the arc-shaped hole 2232A communicates with the aforementioned side groove 2221 , and the arc-shaped hole 2232A is a through hole that penetrates the transition section 223A. That is, the arc-shaped holes 2232A not only limit the circumferential position of the output gear carrier 261A, but also function as a communication hole. In this solution, the second ring gear 22A does not need to have a communication hole.
  • limit bosses 266A are provided in two, and are arranged symmetrically with respect to the central axis of the central hole 2610A.
  • the limit method is not limited to this.
  • the second ring gear may be provided with a limiting protrusion
  • the output gear carrier may be provided with a limiting protrusion
  • the limiting protrusion and the limiting protrusion can also limit the circumferential rotation stroke of the output gear carrier.

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Abstract

本发明所提供的电动阀，齿轮减速机构包括第一齿圈、第二齿圈和沿电动阀的纵向设置的上行星齿轮组件和下行星齿轮组件，至少部分第一齿圈位于转子部件的内腔，转子部件的输入齿轮部与上行星齿轮组件的行星齿轮啮合，下行星齿轮组件与传动杆转动连接。本实施方案中至少部分第一齿圈位于转子部件的内腔，利于减小电动阀的体积。

Description

一种电动阀
本申请要求于2020年12月29日提交中国专利局、申请号为202011600937.4、发明名称为“一种电动阀”，以及于2021年07月28日提交中国专利局、申请号为202110857831.0、发明名称为“一种电动阀”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
本发明涉及流体控制技术领域，具体涉及一种电动阀。
背景技术
图1为背景技术给出的一种电动阀的局部剖面示意图。如图1所示，电动阀包括外壳部件01、转子部件02、齿轮组件03和传动杆04，转子部件02和齿轮组件03位于外壳部件01内腔，齿轮组件03包括齿圈031、太阳齿轮件032、行星齿轮组033和输出齿轮组034。其动作过程如下：转子部件02转动带动太阳齿轮件032转动。太阳齿轮件032转动带动行星齿轮组033转动，行星齿轮组033转动带动输出齿轮组034转动，输出齿轮组034再带动传动杆04转动。该结构的电动阀，将转子部件02输出的小扭矩通过齿轮组件03转换成了较大的输出扭矩，以便带动传动杆04转动实现电动阀的功能。如何优化电动阀的结构，以实现电动阀的小型化为本领域技术人员需要考虑的问题。
发明内容
本发明的目的是提供一种电动阀，包括控制部件、阀体部件和齿轮减速机构，所述控制部件包括转子部件，所述阀体部件包括传动杆，所述齿轮减速机构包括第一齿圈、第二齿圈和沿所述电动阀的纵向设置的上行星齿轮组件和下行星齿轮组件，至少部分所述第一齿圈位于所述转子部件的 内腔，所述转子部件包括输入齿轮部，所述输入齿轮部与所述上行星齿轮组件的行星齿轮啮合，所述上行星齿轮组件的行星齿轮与所述第一齿圈啮合，所述下行星齿轮组件的行星齿轮与所述第二齿圈啮合，所述下行星齿轮组件与所述传动杆转动连接。
本发明所提供的电动阀，齿轮减速机构包括第一齿圈、第二齿圈和沿电动阀的纵向设置的上行星齿轮组件和下行星齿轮组件，至少部分第一齿圈位于转子部件的内腔，转子部件的输入齿轮部与上行星齿轮组件的行星齿轮啮合，下行星齿轮组件与传动杆转动连接。本实施方案中至少部分第一齿圈位于转子部件的内腔，利于减小电动阀的体积。
附图说明
图1：背景技术给出的一种电动阀的剖面示意图；
图2：本发明提供的一种电动阀的剖面示意图；
图3：图2的局部放大示意图；
图4：图2中第二齿圈的结构示意图；
图5a：图2中第一齿圈的半剖立体图；
图5b：图5a中第一齿圈的结构示意图；
图6a：图2中输出齿轮架的立体图一；
图6b：图2中输出齿轮架的立体图二；
图7：图2中第二壳体部的结构示意图；
图8：图2中第二壳体部、第一齿圈及输出齿轮架的配合示意图；
图9：本发明提供的另一种第一齿圈的剖面图；
图10：图9中第一齿圈的结构示意图；
图11：本发明提供的另一种输出齿轮架的结构示意图。
具体实施方式
为了使本技术领域的人员更好地理解本发明方案，下面结合附图和具体实施方式对本发明作进一步的详细说明。
这里需要说明的是，本文中所涉及的上和下等方位词是以图2中零部 件位于图中及零部件相互之间的位置来定义的，只是为了表达技术方案的清楚及方便。应当理解，本文所采用的方位词不应限制本申请请求保护的范围。
还需要说明的是，本文中涉及的“周向转动”是指圆周方向的运动，既包含转动一圈(360°)以上的运动，也包含转动一圈(360°)以内的运动。
图2为本发明提供的一种电动阀的剖面示意图；图3为图2的局部放大示意图；图4为图2中第一齿圈的结构示意图；图5a为图2中第二齿圈的半剖立体图；图5b为图5a中第二齿圈的结构示意图；图6a为图2中输出齿轮架的立体图一；图6b为图2中输出齿轮架的立体图二；图7为图2中第二壳体部的结构示意图；图8为图2中第二壳体部、第二齿圈及输出齿轮架的配合示意图。
如图2、图3所示，电动阀包括控制部件1、齿轮减速机构2、壳体部件3、阀体部件4。电动阀的阀腔包括壳体部件的内腔30和阀体部件的内腔40。阀体部件4包括传动杆41、阀芯42和阀体43。
控制部件1包括线圈11、转子部件12、轴承件13、弹簧14、定位座15和定位杆16。线圈11位于壳体部件3外，转子部件12、轴承件13、弹簧14、定位座15和定位杆16位于壳体部件的内腔30。线圈11通电，能够驱动转子部件12周向旋转。定位座15位于转子部件12的上方，定位杆16的上端位于定位座15的第一盲孔151，定位杆16的下端位于传动杆41的第二盲孔410，以此实现对定位杆16的定位。定位杆16贯穿轴承件13、转子部件12、及齿轮减速机构2的第一级行星齿轮架231、第二级行星齿轮架241、第三级行星齿轮架251，通过定位杆16的定位能够保证转子部件12与齿轮减速机构2的同轴度，提高了转子部件12与齿轮减速机构2之间的传递可靠性。同时，也有利于提高齿轮减速机构2的动作稳定性，降低卡死的风险。具体的，转子部件12具有贯穿孔120，定位杆16贯穿该贯穿孔120，定位杆16与形成贯穿孔120的孔壁1201间隙配合。转子部件12包括支架121、与支架121固定连接的转子122。转子122通过磁粉烧结制成，支架121通过注塑与转子122固定连接，支架121具有前述 贯穿孔120，支架121包括轴部123，轴部123的下段一体设有输入齿轮部1211。轴承件13位于定位座15与支架121之间，弹簧14部分外套于定位座15，弹簧14又一部分外套于轴承件13，弹簧14的一端抵接定位座15，弹簧14的另一端抵接轴承件13，轴承件13抵接支架121。通过设置弹簧14能够对转子部件12施加弹力，避免在电动阀运转过程中因转子部件12的轴向窜动而出现卡死的现象。
齿轮减速机构2设于壳体部件的内腔30。齿轮减速机构2包括第一齿圈21、第二齿圈22、上行星齿轮组件201和下行星齿轮组件202，上行星齿轮组件201包括第一级行星齿轮组23、第二级行星齿轮组24，下行星齿轮组件202包括第三级行星齿轮组25、第四级行星齿轮组26。第一级行星齿轮组23、第二级行星齿轮组24、第三级行星齿轮组25与第四级行星齿轮组26依次沿电动阀的纵向设置。
具体的，第一级行星齿轮组23位于第一齿圈的内腔210，包括第一级行星齿轮架231及安装于第一级行星齿轮架231上的第一级行星齿轮232，前述输入齿轮部1211与第一级行星齿轮232啮合；第二级行星齿轮组24包括第二级行星齿轮架241及安装于第二级行星齿轮架241上的第二级行星齿轮242，第二级行星齿轮架241部分位于第一齿圈的内腔210，另一部分位于第二齿圈的内腔220，第二级行星齿轮242位于第一齿圈的内腔210，第一级行星齿轮架231的太阳齿轮与第二级行星齿轮242啮合。上行星齿轮组件201的行星齿轮包括第一级行星齿轮232和第二级行星齿轮242，第一级行星齿轮232与第二级行星齿轮242模数相同。需要说明的是，在行星齿轮的齿数不变的情况下，模数越大则齿轮的径向尺寸越大。
第三级行星齿轮组25、第四级行星齿轮组26位于第二齿圈的内腔220。第三级行星齿轮组25包括第三级行星齿轮架251及安装于第三级行星齿轮架251上的第三级行星齿轮252，第二级行星齿轮架241的太阳齿轮与第三级行星齿轮252啮合；第四级行星齿轮组26包括输出齿轮架261及安装于输出齿轮架261的立柱263的第四级行星齿轮262，第三级行星齿轮架251的太阳齿轮与第四级行星齿轮262啮合。本实施例中，下行星齿轮组件202的行星齿轮包括第三级行星齿轮252和第四级行星齿轮262，第三 级行星齿轮252与第四级行星齿轮262模数相同。上行星齿轮组件201的行星齿轮的模数小于下行星齿轮组件202的行星齿轮的模数，即第二级行星齿轮242的模数小于第三级行星齿轮252的模数。
本实施方案中，转子部件12的输入齿轮部1211与上行星齿轮组件201的第一级行星齿轮232啮合，第一级行星齿轮232又通过第一级行星齿轮架231将扭矩传递给第二级行星齿轮242，由于上行星齿轮组件201的行星齿轮靠近转子部件12(扭矩输入端)，所承受的负载小，强度要求低，因此可以采用小模数(小尺寸)的行星齿轮；下行星齿轮组件202的行星齿轮靠近传动杆41(扭矩输出端)，所承受的负载大，强度要求高，因此需要采用大模数(大尺寸)的行星齿轮。如此，将上行星齿轮组件的行星齿轮的模数设置得比下行星齿轮组件的行星齿轮的模数小，有利于缩小上行星齿轮组件的行星齿轮的尺寸，利于减小电动阀的横向尺寸，从而减小电动阀的体积。
输出齿轮架261包括中心孔2610，该中心孔2610的横截面轮廓为非圆形，传动杆41上端伸入中心孔2610实现与输出齿轮架261的转动连接，输出齿轮架261能够带动传动杆41转动。传动杆41与阀芯42转动连接，传动杆41能够带动阀芯42转动以实现电动阀的开阀、关阀或流量调节功能。
本实施例中，第一齿圈21的内壁设有沿第一齿圈21的纵向延伸的第一内齿214，第一级行星齿轮232与第二级行星齿轮242都通过第一内齿214与第一齿圈21啮合。第二齿圈22的内壁设有轴向延伸的第二内齿2211，第三级行星齿轮252与第四级行星齿轮262都通过第二内齿2211与第二齿圈22啮合。
由于上行星齿轮组件201的第一级行星齿轮组23、第二级行星齿轮组24靠近转子部件12，传动扭矩小，强度要求低。同样的，与第一级行星齿轮组23、第二级行星齿轮组24配合的第一齿圈21强度要求低。因此，第一级行星齿轮架231、第一级行星齿轮232、第二级行星齿轮架241及第二级行星齿轮242可采用塑料制成，具体由尼龙、PPS、PEEK等材料注塑成型。
壳体部件3包括第一壳体部31、第二壳体部32和线圈安装架33，第一壳体部31和第二壳体部32分别由不锈钢板材或管材拉伸制成，第一壳体部31与第二壳体部32通过焊接固定，第一壳体部31与线圈安装架33通过焊接固定，第二壳体部32与阀体43焊接固定。具体的，转子部件12位于第一壳体部的内腔310，线圈11外套第一壳体部31并与线圈安装架33固定。第一壳体部31包括等径段311和扩径段312，如图3所示，等径段311的壁厚小于第二壳体部32的壁厚，转子部件12位于等径段311内，前述线圈11外套等径段311。第二壳体部32的上段设有外台阶部321，扩径段312置于外台阶部321，且扩径段312的下端部与外台阶部321焊接固定。设置外台阶部321，其有益效果在于，第一壳体部31与第二壳体部32焊接时容易定位，能够提高焊接质量。
等径段311的壁厚小于第二壳体部32的壁厚,其有益效果在于，等径段311的壁厚设置得较薄有利于提高磁通量，提高线圈11的驱动效率，降低能耗；第二壳体部32的壁厚设置得较厚有利于增加耐压强度，提高使用寿命，即使受到较强的冷媒冲击力也不易损坏。
进一步的，如图2所示，第二壳体部32的下段包括缩径部322，缩径部322呈圆筒状，阀体部件4的阀体43包括朝控制部件1方向凸出的凸出部431，凸出部431呈圆筒状，缩径部322至少部分位于凸出部431的内腔，缩径部322与凸出部431焊接固定。可以想到的是，凸出部431也可以至少部分位于缩径部322的内腔。
进一步的，如图2、图3、图4所示，本实施例中，第一齿圈21大致呈圆筒状，第一齿圈21由塑料制成，具体由尼龙、PPS、PEEK等材料注塑成型。第一齿圈21位于第一壳体部31的内腔310，同时，第一齿圈21至少部分位于转子部件12的内腔，第一齿圈21置于第二齿圈22上方。第一齿圈21包括支撑部211、定位部212和卡接部213，支撑部211位于定位部212上方，定位部212位于卡接部213上方，定位部212的外径大于支撑部211的外径，卡接部213的外径大于定位部212的外径。支撑部211至少部分位于转子122的内腔1220，定位部212位于转子122的下方。将至少部分支撑部211伸入转子122的内腔1220，能够减少电动阀的轴向尺 寸，利于减小电动阀的体积，实现小型化。支撑部211包括通孔2110，支撑部211在电动阀的纵向支撑转子部件12。支架121的轴部123贯穿支撑部的通孔2110并伸入第一齿圈21的内腔210，轴部123包括输入齿轮部1211，输入齿轮部1211位于第一齿圈21的内腔210并与第一级行星齿轮232啮合，轴部123与支撑部211的形成通孔2110的孔壁2111间隙配合。如此设置，提高了转子部件12与齿轮减速机构2之间的传递可靠性。
具体的，支架121包括台阶面朝下的下台阶部1212，输入齿轮部1211位于下台阶部1212的下方，下台阶部1212的台阶面1214与支撑部211的上端面2112相接触，下台阶部1212的台阶壁1213与形成通孔2110的孔壁2111间隙配合，支撑部211与下台阶部1212配合可旋转地支撑支架121，即转子部件12能够相对于第一齿圈21周向转动。
定位部212的外壁与第一壳体部31的等径段311的内壁间隙配合。此处的“间隙配合”是指具有间隙(包括最小间隙等于零)的配合，本实施方案中，具体的，定位部212的外周壁与第一壳体部31的等径段311的内壁的间隙0≤g＜0.2mm。定位部212为沿第一齿圈21的轴向延伸的若干肋部，相邻肋部之间形成凹槽，如此，能够节省材料、降低第一齿圈21的重量。卡接部213包括第一凹部2131，第二齿圈22包括朝控制部件1方向凸出的第一凸起部2212，第一凸起部2212位于第二齿圈22的上端，第一凸起部2212与第一凹部2131凹凸配合以限制第一齿圈21的周向转动，即第一齿圈21与第二齿圈22周向限位连接。
当然，可以想到的是，相反的，卡接部213可以设置凸部，第二齿圈22可以设置凹部，同样通过凹凸配合实现周向限位。或者，第一齿圈21与第二齿圈22也可以通过焊接固定连接。
更进一步，还包括弹性件5，在电动阀的纵向，弹性件5设于第一壳体部31的扩径段312与卡接部213之间，并弹性抵接于扩径段312的内壁与卡接部213的上端面之间，以防止第一齿圈21、第二齿圈22轴向窜动。这里的弹性件5可以是如图2中所示的橡胶等非金属材料制的弹性圈，也可以是金属材料制的金属弹片。通过定位杆16对第一齿圈21进行径向限位，第二壳体部32对第二齿圈22进行周向限位(本实施例以第二壳体部 32和第二齿圈22凹凸配合以实现周向限位，后有详述)，第二齿圈22对第一齿圈21进行周向限位，第一壳体部31对第一齿圈21进行轴向限位，无需焊接即能够实现对第一齿圈21、第二齿圈22的定位，这种方式零部件组装简单，无需焊接。
如图5a、图8所示，第二齿圈22为一体结构，大致呈上大下小的圆筒状，由金属粉末冶金制成。第二齿圈22包括大径段221和小径段222，前述第二内齿2211设于大径段221的内周壁，前述第一凸起部2212设于大径段221的上端。大径段221包括第二凸起部2213，第二凸起部2213自大径段221的外周壁径向向外凸出。第二壳体部32的外台阶部321的台阶壁3211包括第二凹部3210，第二凸起部2213与第二凹部3210凹凸配合以限制第二齿圈22周向转动。本实施例中，由于第二齿圈22由金属粉末冶金制成，制作时第二内齿2211、第一凸起部2212和第二凸起部2213一体成型，加工方便，第二壳体部32由金属板材或管材拉伸制成，第二凹部3210只需车加工即可，加工方便。另，第二齿圈22与第二壳体部32通过凹凸配合进行定位，装配简单。
当然，可以想到的是，相反的，第二齿圈22可以设置凹部，第二壳体部32可以设置凸部，同样通过凹凸配合实现周向限位。或者，第二齿圈22与第二壳体部32也可以通过焊接固定连接。
进一步的，如图2、图5a、图8所示，小径段222至少部分位于第二壳体部32的缩径部322的内腔。第二齿圈22包括沿电动阀的纵向延伸的贯通孔2201，传动杆41贯穿该贯通孔2201，并与形成贯通孔2201的孔壁间隙配合，传动杆41能够相对于第二齿圈22转动。传动杆41的上端位于壳体部件的内腔30，传动杆41的下端位于阀体部件的内腔40。其有益效果在于，第二齿圈32由具有自润滑性的金属材料粉末冶金制成，使得传动杆41转动时摩擦阻力小，且能够减少传动轴41在转动过程中的磨损，提高其使用寿命。本实施方案中第二齿圈32集成了轴承的功能，无需单独设置轴承，减少了零部件数量。
进一步的，如图5a、图6a、图6b及图8所示，第二齿圈22还包括过渡段223，过渡段223位于大径段221与小径段222之间，输出齿轮架261 置于过渡段223上方，上述第二齿圈22的贯通孔2201包括小径段222的内孔2220和过渡段223的内孔2230。
第二齿圈22还包括限位凸部2231，限位凸部2231自过渡段223朝控制部件1方向凸出。进一步的，限位凸部2231与大径段221的内周壁相连，金属粉末冶金时，限位凸部2231一体成型于第二齿圈22。输出齿轮架261的朝向阀体部件4的一侧包括限位凹槽264，限位凸部2231至少部分位于限位凹槽264，限位凸部2231能够与限位凹槽264的两个槽壁266抵接以限制输出齿轮架261的转动行程，也就是限制了传动轴41的转动行程，如此设置可限制阀芯42的转动行程，实现电动阀的全开、全关及流量调节功能。需要说明的是，本实施方案中的电动阀的阀芯采用球状阀芯，若定义电动阀在全关状态下阀芯角度为0°，则当阀芯转动90°达到全开状态，即限位凹槽264的两个槽壁266限定了输出齿轮架261转动的最大行程为90°。本实施例中，阀芯42大致呈球状，但也可以不限于球状，例如半球形、纺锤形。
进一步的，上述限位凸部2231设置为2个，且相对小径段222的通孔2220的中心轴线对称设置，相应地，与限位凸部2231配合的限位凹槽264也设置为2个。如此设置，有利于输出齿轮架261周向转动平稳、限位可靠。
输出齿轮架261的朝向阀体部件4的一侧还包括第三凸起部265，第三凸起部265的下端部大致呈圆弧状或平台状，第三凸起部265抵接过渡段223。通过设置第三凸起部265能够减小输出齿轮架261与过渡段223的接触面积，从而能够降低输出齿轮架261的磨损，提高其使用寿命。
如图8所示，传动杆41包括凸缘部411，凸缘部411位于第二齿圈22的小径段222的下方，凸缘部411能够与小径段222的下端抵接以限制传动杆41轴向向上移动，如此能够防止传动杆41将输出齿轮架261顶歪，影响减速齿轮机构2的可靠传动。
进一步的，第二齿圈22包括连通通道200，连通通道200连通第二齿圈22的内腔220和阀体部件的内腔40。连通通道200包括连通孔2230和侧槽2221，连通孔2230与侧槽2221连通，连通孔2230设于过渡段223， 连通孔2230贯穿过渡段223，侧槽2221设于小径段222的外周壁，侧槽2221沿第二齿圈22的纵向延伸。通过设置连通通道200，将流体引入第二齿圈22的内腔220，能够增强电动阀的内部循环，对齿轮减速机构2进行润滑和散热，增加其使用寿命。
图9为本发明提供的另一种第二齿圈的剖面图；图10为图9中第二齿圈的结构示意图；图11为本发明提供的另一种输出齿轮架的结构示意图。
如图9、图10、图11所示，本实施例与上述实施例的不同之处主要在于第二齿圈和输出齿轮架的配合结构。
第二齿圈22A包括过渡段223A，输出齿轮架261A置于过渡段223A。过渡段223A包括弧形孔2232A，如图10所示，弧形孔2232A具体为圆弧状通孔，当然也可以是圆弧状盲孔。输出齿轮架261A的朝向阀体部件4的一侧包括限位凸台266A，限位凸台266A至少部分位于弧形孔2232A内，限位凸台266A能够与形成弧形孔2232A的两个端壁2233A抵接以限制输出齿轮架261A的转动行程，也就是限制了传动轴41的转动行程，如此设置可限制阀芯42的转动行程，实现电动阀的全开、全关及流量调节功能。需要说明的是，本实施方案中的电动阀的阀芯采用球状阀芯，若定义电动阀在全关状态下阀芯角度为0°，则当阀芯转动90°达到全开状态，即弧形孔2232A的两个端壁2233A限定了输出齿轮架261A转动的最大行程为90°。
如图10所示，本实施例与上述实施例的不同之处还在于第二齿圈的连通通道的设置。
本实施方案中，第二齿圈22A包括连通通道200A，连通通道200A连通第二齿圈的内腔220和阀体部件的内腔40。连通通道200A包括弧形孔2232A和前述侧槽2221，弧形孔2232A与前述侧槽2221连通，弧形孔2232A为通孔，其贯穿过渡段223A。即弧形孔2232A不仅对输出齿轮架261A进行周向限位，也具有连通孔的功能，该方案中第二齿圈22A无需特意开设连通孔。
进一步的，上述限位凸台266A设置为2个，且相对中心孔2610A的中心轴线对称设置，相应地，与限位凸台266A配合的弧形孔2232A也设置为 2个。如此设置，有利于输出齿轮架261A周向转动平稳、限位可靠。
当然，限位方式不仅限于此。作为一种变形例，也可以是第二齿圈设置限位凸部，输出齿轮架设置限位凸台，限位凸台与限位凸部配合也能限制输出齿轮架的周向转动行程。
本文中应用了具体个例对本发明的原理及实施方式进行了阐述，以上实施例的说明只是用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 (12)

  1. 一种电动阀，其特征在于，包括控制部件、阀体部件和齿轮减速机构，所述控制部件包括转子部件，所述阀体部件包括传动杆，所述齿轮减速机构包括第一齿圈、第二齿圈和沿所述电动阀的纵向设置的上行星齿轮组件和下行星齿轮组件，至少部分所述第一齿圈位于所述转子部件的内腔，所述转子部件包括输入齿轮部，所述输入齿轮部与所述上行星齿轮组件的行星齿轮啮合，所述上行星齿轮组件的行星齿轮与所述第一齿圈啮合，所述下行星齿轮组件的行星齿轮与所述第二齿圈啮合，所述下行星齿轮组件与所述传动杆转动连接。
  2. 如权利要求1所述的电动阀，其特征在于，所述转子部件包括转子和支架，所述转子和支架固定连接，至少部分所述第一齿圈位于所述转子的内腔，所述第二齿圈位于所述转子的下方，所述支架包括所述输入齿轮部，所述上行星齿轮组件的行星齿轮的模数小于所述下行星齿轮组件的行星齿轮的模数。
  3. 如权利要求1所述的电动阀，其特征在于，所述上行星齿轮组件包括第一级行星齿轮组和第二级行星齿轮组，所述下行星齿轮组件包括第三级行星齿轮组和第四级行星齿轮组，至少部分所述第一级行星齿轮组位于所述转子部件的内腔，所述第一级行星齿轮组和部分所述第二级行星齿轮组位于所述第一齿圈的内腔，所述第三级行星齿轮组、所述第四级行星齿轮组和另一部分所述第二级行星齿轮组位于所述第二齿圈的内腔。
  4. 如权利要求3所述的电动阀，其特征在于，所述第一齿圈包括第一内齿，所述第一级行星齿轮组的第一级行星齿轮、所述第二级行星齿轮组的第二级行星齿轮分别与所述第一内齿啮合；所述第二齿圈包括第二内齿，所述第三级行星齿轮组的第三级行星齿轮、所述第四级行星齿轮组的第四级行星齿轮分别与所述第二内齿啮合，所述上行星齿轮组件的行星齿轮包括所述第一级行星齿轮和所述第二级行星齿轮，所述第一级行星齿轮的模数与所述第二级行星齿轮的模数相同，所述下行星齿轮组件的行星齿轮包括所述第三级行星齿轮和所述第四级行星齿轮，所述第三级行星齿轮的模数与所述第四级行星齿轮的模数相同。
  5. 如权利要求2所述的电动阀，其特征在于，还包括壳体部件，所述转子部件、所述上行星齿轮组件和所述下行星齿轮组件位于所述壳体部件的内腔，所述支架包括台阶面朝下的下台阶部，所述输入齿轮部位于所述下台阶部的下方，所述第一齿圈包括支撑部，所述支撑部包括通孔，所述下台阶部的台阶面与所述支撑部的上端面相接触，所述下台阶部的台阶壁与形成所述通孔的孔壁间隙配合，所述支撑部至少部分位于所述转子的内腔。
  6. 如权利要求5所述的电动阀，其特征在于，所述第一齿圈还包括定位部，所述支撑部位于所述定位部上方，所述转子位于所述定位部上方，所述定位部的外径大于所述支撑部的外径，所述定位部的外壁与所述壳体部件的内壁间隙配合。
  7. 如权利要求6所述的电动阀，其特征在于，所述壳体部件包括第一壳体部和第二壳体部，所述第一壳体部包括等径段和扩径段，所述转子部件位于所述等径段内，所述定位部的外壁与所述等径段的内壁间隙配合，所述控制部件的线圈外套所述等径段，所述扩径段与所述第二壳体部固定连接。
  8. 如权利要求6所述的电动阀，其特征在于，所述第一齿圈还包括卡接部，所述卡接部的外径大于所述定位部的外径，所述卡接部包括第一凹部，所述第二齿圈包括朝所述控制部件方向凸出的第一凸起部，所述第一凸起部与所述第一凹部凹凸配合；或所述卡接部包括朝所述阀体部件方向凸出的第一凸起部，所述第二齿圈包括第一凹部，所述第一凸起部与所述第一凹部凹凸配合。
  9. 如权利要求8所述的电动阀，其特征在于，所述第二齿圈包括大径段和小径段，所述第一凸起部设于所述大径段的上端，所述大径段包括自其外周壁径向向外凸出的第二凸起部，所述第二壳体部的上段包括第二凹部，所述第二凸起部与所述第二凹部凹凸配合，所述第二壳体部的下段包括缩径部，所述小径段至少部分位于所述缩径部的内腔，所述小径段与所述缩径部间隙配合，所述缩径部与所述阀体部件的阀体固定连接。
  10. 如权利要求1-9任一项所述的电动阀，其特征在于，所述控制部 件还包括定位座和定位杆，所述定位座位于所述转子部件上方，所述定位杆贯穿所述转子部件的贯穿孔，所述定位杆与形成所述贯穿孔的孔壁间隙配合，所述定位杆的上端位于所述定位座的第一盲孔，所述定位杆的下端位于所述传动杆的第二盲孔。
  11. 如权利要求10所述的电动阀，其特征在于，所述定位杆贯穿所述上行星齿轮组件的第一级行星齿轮架、第二级行星齿轮架和所述下行星齿轮组件的第三级行星齿轮架、输出齿轮架，所述输出齿轮架与所述传动杆转动连接。
  12. 如权利要求1-9任一项所述的电动阀，其特征在于，所述第一齿圈和所述上行星齿轮组件由塑料材料制成。
PCT/CN2021/139971 2020-12-29 2021-12-21 一种电动阀 WO2022143289A1 (zh)

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JP2006029435A (ja) * 2004-07-15 2006-02-02 Saginomiya Seisakusho Inc 電動式コントロールバルブおよび冷凍サイクル装置
CN101067462A (zh) * 2006-05-02 2007-11-07 株式会社不二工机 电动阀
CN109869488A (zh) * 2017-12-01 2019-06-11 浙江三花智能控制股份有限公司 电子膨胀阀及具有其的制冷系统
CN110388496A (zh) * 2018-04-19 2019-10-29 浙江三花汽车零部件有限公司 球阀
CN111148928A (zh) * 2017-09-28 2020-05-12 株式会社不二工机 电动阀
CN211738083U (zh) * 2019-11-20 2020-10-23 浙江三花制冷集团有限公司 一种电动阀

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JP2006029435A (ja) * 2004-07-15 2006-02-02 Saginomiya Seisakusho Inc 電動式コントロールバルブおよび冷凍サイクル装置
CN101067462A (zh) * 2006-05-02 2007-11-07 株式会社不二工机 电动阀
CN111148928A (zh) * 2017-09-28 2020-05-12 株式会社不二工机 电动阀
CN109869488A (zh) * 2017-12-01 2019-06-11 浙江三花智能控制股份有限公司 电子膨胀阀及具有其的制冷系统
CN110388496A (zh) * 2018-04-19 2019-10-29 浙江三花汽车零部件有限公司 球阀
CN211738083U (zh) * 2019-11-20 2020-10-23 浙江三花制冷集团有限公司 一种电动阀

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