CN114688303B

CN114688303B - Electric valve

Info

Publication number: CN114688303B
Application number: CN202011629224.0A
Authority: CN
Inventors: 请求不公布姓名
Original assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Current assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Priority date: 2020-12-31
Filing date: 2020-12-31
Publication date: 2023-12-05
Anticipated expiration: 2040-12-31
Also published as: CN114688303A

Abstract

The electric valve is characterized by comprising a valve body, wherein the valve body comprises a valve seat assembly, a sun gear, a fixed gear, a gear slider, a planetary gear set and a valve shaft; the valve seat assembly is fixedly connected or in limiting connection with the valve shaft, and the valve seat assembly is fixedly connected with the sleeve part; the planetary gear set comprises at least three planetary gears, and any planetary gear comprises a large-diameter gear and a small-diameter gear; the gear slide block comprises a slide block gear part which is meshed with the small-diameter gear; the fixed gear comprises a fixed gear body and a fixed gear bracket, the fixed gear bracket is made of metal materials, and the fixed gear bracket is fixedly welded with the valve seat assembly; the number of teeth of the fixed gears is 48, the number of teeth of the large-diameter gears is 18, and the number of teeth of the small-diameter gears is 12. According to the electric valve provided by the embodiment of the application, each gear can be smoothly meshed during assembly, so that the assembly of a gear assembly is convenient.

Description

Electric valve

[ field of technology ]

The application relates to the technical field of refrigeration control, in particular to an electric valve.

[ background Art ]

Refrigerating and refrigerating equipment such as a refrigerator is widely applied to various occasions, taking the refrigerator as an example, each temperature zone of the refrigerator is controlled according to a certain zone of preset temperature, namely intermittent refrigeration is performed, and when the preset temperature is reached, the compressor is stopped; when the actual temperature of the temperature zone is higher than the preset temperature, the compressor is started to refrigerate, so that the temperature of the temperature zone reaches the preset temperature. When the compressor is restarted after stopping, larger starting power consumption is generated, and the high-temperature refrigerant is heated up first in the initial stage of starting, and is cooled after reaching the condition of refrigeration cycle, and the throttling is realized by adopting a capillary tube.

[ application ]

It is an object of one of the embodiments of the present application to provide an electric valve employing a planetary gear mechanism, which can facilitate assembly of gears. For this purpose, one embodiment of the present application adopts the following technical scheme:

the electric valve is characterized by comprising a valve body, wherein the valve body comprises a valve seat assembly, a sun gear, a fixed gear, a gear slider, a planetary gear set and a valve shaft; the valve seat assembly is fixedly connected or in limiting connection with the valve shaft, and the valve seat assembly is fixedly connected with the sleeve part;

the planetary gear set comprises at least three planetary gears, and any planetary gear comprises a large-diameter gear and a small-diameter gear; the gear slide block comprises a slide block gear part which is meshed with the small-diameter gear;

the fixed gear comprises a fixed gear body and a fixed gear bracket, the fixed gear bracket is made of metal materials, and the fixed gear bracket is fixedly welded with the valve seat assembly;

the number of teeth of the fixed gears is 48, the number of teeth of the large-diameter gears is 18, and the number of teeth of the small-diameter gears is 12.

According to the electric valve provided by the embodiment of the application, a planetary gear speed reduction system is adopted, the number of teeth of the fixed gears is 48, the number of teeth of the large-diameter gears is 18, and the number of teeth of the small-diameter gears is 12. And each gear can be smoothly meshed during assembly, so that the assembly of the gear assembly is convenient.

[ description of the drawings ]

FIG. 1 is a schematic cross-sectional view of an embodiment of the present application;

FIG. 2 is a top view of the valve seat assembly provided in this embodiment in engagement with first and second fittings and a valve shaft;

FIG. 3 is a view A-A of FIG. 2;

FIG. 4 is a perspective view of the valve seat assembly provided in this embodiment in combination with the first adapter and the second adapter and the valve shaft;

FIG. 5 is a schematic perspective view of a fixed gear assembly according to one embodiment of the present application;

FIG. 6 is a cross-sectional view of a stationary gear assembly provided in accordance with one embodiment of the present application;

FIG. 7 is a schematic view of the front view of the gear slider according to the first embodiment of the present application;

FIG. 8 is a schematic view of the reverse side view of the gear slider according to the first embodiment of the present application;

FIG. 9 is a schematic structural view of a planetary gear set provided by the first embodiment;

FIG. 10 is a schematic diagram of an assembled state of a planetary gear set according to one embodiment of the present application;

FIG. 11 is a schematic illustration of the relationship between the gear slider and the valve seat assembly when the valve is in the fully closed state;

FIG. 12 is a schematic illustration of the relationship between the gear slider and the valve seat assembly when the electrically operated valve is in an intermediate state of flow regulation;

FIG. 13 is a schematic view of the relationship between the gear slider and the valve seat assembly when the valve is in the fully open flow state;

FIG. 14 is a schematic diagram of a refrigeration system;

fig. 15 is a flow chart of a refrigeration system.

[ detailed description ] of the application

In order to make the technical solution of the present application better understood by those skilled in the art, the present application will be further described in detail with reference to the accompanying drawings and specific embodiments.

Referring to fig. 1 in particular, fig. 1 is a schematic cross-sectional view of an embodiment of the present application. As shown in fig. 1, the electric valve provided in the present embodiment includes a valve body 1 and a stator coil (not shown in the figure). The valve body 1 includes a valve seat assembly 11, a rotor 12, and a valve shaft 14. The stator coil of the electric valve is connected with a drive controller, and after the drive controller is electrified, a pulse drive signal is sent to the stator coil, and the stator coil generates a periodically-changing magnetic field, so that the rotor 12 of the electric valve is driven to rotate in the forward direction or the reverse direction.

The rotor 12 is fixedly connected with the sun gear 13, so that when the rotor 12 rotates, the sun gear 13 can be driven to rotate synchronously, and in the embodiment, the rotor 12 and the sun gear 13 are fixedly connected, and of course, the limit connection can be set, and only the requirement that the rotor 12 can drive the sun gear 13 to rotate together is met. The sun gear 13 is provided with a through hole penetrating through the center thereof, the valve shaft 14 penetrates through the through hole, the sun gear 13 can freely rotate around the valve shaft 14, one end of the valve shaft 14 is fixedly connected with the valve seat assembly 11, the other end of the valve shaft 14 is fixedly connected with the shaft sleeve 16 arranged at the top of the valve body, and of course, the valve shaft 14 can be directly fixedly connected with the shell, so that the valve shaft 14 can provide good concentricity for rotation of the rotor 12 and the sun gear 13.

The electric valve includes a sleeve member, and in this embodiment, the sleeve member includes a first sleeve member 151 and a second sleeve member 152, the first sleeve member 151 is substantially in a sleeve shape having one end opened, and may be made of a stainless steel material, having a first top wall portion 1511 and a first side wall portion 1512, and the second sleeve member 152 is substantially in a sleeve shape having both ends opened, and may be made of a stainless steel material, having a second top wall portion 1521 and a second side wall portion 1522. The diameter of the second side wall portion of the second sleeve member is larger than the diameter of the first side wall portion of the first sleeve member such that the lower end portion of the first sleeve member 151 is secured in engagement with the top wall portion of the second sleeve member 152, such as by welding. The lower edge portion of the second sidewall portion 1522 of the second sleeve member 152 is fixedly attached to the valve seat assembly 11, such as by welding. Of course, fig. 1 shows a specific structure and connection manner of the first sleeve member and the second sleeve member as a specific embodiment, and those skilled in the art may also change the specific structure and connection manner, for example, the second sleeve member is not provided with the second top wall portion 1521, but is provided as an equal-diameter sleeve with two open ends, and a bottom wall portion extending outwards along the radial direction is provided at the bottom of the first sleeve member, and then is fixedly connected with the second sleeve member, so that the connection relationship may also be achieved. Alternatively, instead of the first sleeve member and the second sleeve member being separately formed, the first side wall portion 1512, the second side wall portion 1522, the first top wall portion 1511, and the second top wall portion 1521 may be formed simultaneously by, for example, one-shot press forming using a metal plate.

One end of the sleeve 16 is limited or fixedly connected to the valve shaft 14, the other end of the sleeve 16 abuts against the first top wall portion 1511, and the edge of the sleeve 16 may abut against the first side wall portion 1512, as shown in fig. 1, and the sleeve 16 ensures that the axis of the valve shaft substantially coincides with the central axis of the valve body. A spring 17 is arranged between the shaft sleeve 16 and the sun gear 13, and the spring 17 can provide a certain pretightening force for the sun gear 13 to restrain the sun gear 13 from being excessively displaced upwards. In the present embodiment, the lower end of the spring is abutted against the sun gear in the connection mode of the sun gear 13 and the rotor 12, but since the sun gear and the rotor can be regarded as one unit, there are various combinations in terms of the structure, and therefore, the lower end of the spring may be abutted against the rotor.

In the valve cavity enclosed by the first sleeve part, the second sleeve part and the valve seat assembly, a planetary gear set 18, a fixed gear 19 and a gear slide block 20 are also arranged, and the main working principle is as follows: the rotor and the sun wheel rotate to drive the planetary gears of the planetary gear set to rotate, and the planetary gears drive the valve block gears to rotate while rotating so as to change the positions of the valve block gears relative to the valve seat assembly, thereby achieving the purpose of controlling flow. The structure of the valve seat assembly, planetary gear set, fixed gear, valve block gear, and connection or mating relationship will be described below.

Referring to fig. 2, 3 and 4, fig. 2 is a top view of a valve seat assembly and first and second connection pipes and a valve shaft according to the present embodiment, fig. 3 is a view A-A of fig. 2, and fig. 4 is a perspective view of a valve seat assembly and first and second connection pipes and a valve shaft according to the present embodiment. The valve seat assembly 11 provided in this embodiment includes a valve seat body portion 111 and a diaphragm portion 112. The electric valve further includes a first adapter tube 114 and a second adapter tube 115, and the valve seat body portion 111 is fixedly assembled with the first adapter tube 114 and the second adapter tube 115. The first connection pipe 114 and the second connection pipe 115 are respectively used as inflow or outflow passages of fluid media of the electric valve, and are generally used for being installed in a refrigerating system, a freezer, an air conditioner and the like to be connected with a system pipeline.

The valve seat body 111 is provided with a mounting hole 1111, and in this embodiment, the mounting hole 1111 is a blind hole structure, that is, does not penetrate the valve seat body 111, and after assembly, the valve shaft 14 is inserted into the mounting hole 1111 to be fixed. The valve seat body portion 111 is located the opposite side of mounting hole portion 1111, still is provided with first takeover installation department 1112 and second takeover installation department 1113, and first takeover installation department 1112 and second takeover installation department 1113 are the through-hole that runs through the upper and lower surface of first plate body portion 111, and first takeover 114 is through first takeover installation department 1112 and first plate body portion 111 fixed connection, and second takeover 115 is through second takeover installation department 1113 and first plate body portion 111 fixed connection. In this embodiment, the through holes of the first pipe mounting portion 1112 and the second pipe mounting portion 1113 are stepped, and the stepped portion can play a role in positioning when the first pipe and the second pipe are mounted, that is, the first pipe 114 is inserted into the first pipe mounting portion 1112 and then abuts against the stepped portion, so that the depth of insertion is ensured. The outer edge of the valve body 111 is provided with a first step 1114 and a second step 1115, and when assembled, the second sidewall 1522 of the second sleeve member may be positioned and engaged against the first step 1114, and may be specifically fixedly connected by welding. The second step 1115 is for positioning and mating with a fixed gear assembly described below.

The valve seat body 111 is further provided with a flow rate adjusting portion 1116 and a valve port portion 1117, the flow rate adjusting portion 1116 is provided on the upper surface of the valve seat body 111, that is, the mating surface 1134, the flow rate adjusting portion 1116 is recessed inward with respect to the mating surface 1134 to form a groove-like structure which does not penetrate, one end of the groove is connected to the valve port portion 1117, the valve port portion 1117 is formed to penetrate the valve seat body and can communicate with the interior of the first adapter 114, and fluid can flow from the second adapter 115 into the valve cavity of the electric valve, along the flow rate adjusting portion 1116, and out of the first adapter 114 from the valve port portion 1117. The valve opening 1117 forms a flow hole penetrating the valve seat body 111, and forms a valve opening contour 1117a with the mating surface 1134. On one side of the valve port 1117, an inwardly recessed flow adjustment portion 1116 is formed in the mating surface 1134, the flow adjustment portion 1116 has an overall elongated arcuate slot shape, and the first curve 1116a and the second curve 1116b define edge lines of the flow adjustment portion 1116. The first curve 1116a may be an archimedean spiral or a circular arc, and one end of the first curve 1116a intersects the valve port contour 1117a of the valve port 1117 at the mating surface 1134 at point B. The second curve 1116b may be an archimedean spiral, and one end of the second curve 1116b intersects the valve port contour 1117a at point C. Thus, the distance between the first curve 1116a and the second curve 1116b increases gradually in the direction approaching the valve port portion 1117. The flow rate adjusting part 1116 has a smaller overall size, and is particularly suitable for precisely adjusting a small flow rate, such as the flow rate of a refrigerant of a refrigerating system of a refrigerator, compared with a flow rate adjusting valve which is generally in a needle valve structure. The gear slider, described below, can engage the mating surface 1134 and rotate relative to the valve seat body portion to vary the through-flow cross-sectional area of the flow adjustment portion.

Further, the depth of the flow rate adjustment portion 1116 may be set so that the depth of the flow rate adjustment portion 1116 gradually increases along the extending direction of the valve port portion 1117, and in a specific embodiment, the depth H1 of the flow rate adjustment portion 1116 at the end near the valve port portion 1117 satisfies: 0.3mm < H1 < 0.7mm, and at the end near the third curve 1116c, the depth H2 of the flow rate adjustment section 1116 satisfies: h2 is more than 0.05mm and less than 0.15mm. Thus, the small flow can be realized to expand the adjustment range, and the flow adjustment approaches to linear change. In actual operation, the width and depth of the flow adjusting portion 1116 may be set accordingly according to the requirement of the system flow, so as to meet different requirements.

The partition plate 112 is substantially in a plate-shaped structure and may be formed by powder metallurgy, and includes a partition plate body 1123, where the partition plate body 1123 is provided with a plurality of partition plate through holes 1121 penetrating up and down, and a partition plate boss 1122 is provided protruding upward on one surface of the partition plate through holes for limiting the start of the gear slider 20. The diaphragm portion 112 and the valve seat body portion 111 may be fixed by welding such that the second adapter tube mounting portion 1113 is opposed to the diaphragm body 1123 in the axial direction, or at least partially opposed to the diaphragm body 1123. The separator body 1123 described herein refers to a solid portion excluding the separator portion through-hole 1121. In the present embodiment, the second pipe receiving portion is disposed entirely opposite to the partition plate body 1123, so that the high-pressure refrigerant flowing in from the second pipe receiving portion 115 is not directly injected into the valve cavity but is blocked by the partition plate body 1123, and therefore, the gear slider 20 that slides in contact with the surface of the valve seat body 111 is not directly subjected to the impact force of the high-pressure refrigerant, which is advantageous in improving the operation stability of the electric valve. After the diaphragm 112 and the valve seat body 111 are fixed, a substantially annular flow passage 116 is formed therebetween, and the high-pressure refrigerant flows from the second connection pipe 115, is blocked and buffered by the diaphragm body 1123, enters the flow passage 116, and flows into the valve chamber of the electric valve through the plurality of diaphragm through holes 1121.

The partition board boss 1122 is used for initially limiting the gear slider 20, specifically, as shown in a shadow triangle in fig. 2, and is formed by connecting a central axis of the valve seat mounting hole 1111, a central axis of the valve port 1117 and one end point of the partition board boss 1122 in a certain cross section, and this arrangement has the advantage that, since the relative positions of the valve seat mounting hole 1111 and the valve port 1117 are fixed, the relative positions of the partition board boss 1122 and the valve seat can be positioned by a fixture, so that the illustrated shadow triangle always keeps consistent, namely, the three points determine the relative positions, in other words, when mass production is performed, the partition board 112 can always keep the same relative position with the valve seat body 111, so that the relative positions of the gear slider 20 and the valve port 1117 are ensured, the consistency of the product is relatively good, and the flow control of the electric valve is more accurate.

Referring to fig. 5 and 6, fig. 5 is a schematic perspective view of a fixed gear assembly according to an embodiment of the application, and fig. 6 is a cross-sectional view of a fixed gear assembly according to an embodiment of the application. The fixed gear 19 includes a fixed gear body 191 and a fixed gear bracket 192. As shown in fig. 5, the fixed gear bracket 192 may be manufactured using stainless steel tubing or sheet metal stamping roll welding. Specifically, the fixed gear holder 192 has a substantially thin hollow cylindrical shape, and a plurality of holder through-hole portions 1921 are formed in the upper peripheral wall of the fixed gear holder 192 with reference to fig. 5, and the holder through-hole portions 1921 may be formed by punching. The fixed gear carrier has a carrier upper end face 1922 and a carrier lower end face 1923, wherein the carrier lower end face 1923 abuts the second step 1115 after assembly to achieve downward limiting of the axial position of the fixed gear. The fixed gear bracket 192 may be fixedly coupled to the valve seat body portion 111 by welding, such as laser welding.

The fixed gear body 191 is generally circular and may be manufactured by injection molding. That is, the fixed gear bracket 192 may be placed in a preset mold, the fixed gear body 191 is molded by injection molding, and due to the arrangement of the bracket through hole 1921, the corresponding protruding portion 1911 is formed on the outer peripheral wall of the fixed gear body, and the protruding portion 1911 is tightly combined with the bracket through hole 1921, so that the fixed gear body 191 and the fixed gear bracket 192 are fixedly connected into a whole, and are not easy to loosen or fall off. The inner edge of the stationary gear body 191 is a stationary tooth 1912 for meshing with the planetary gear set 18 described below.

The fixed gear assembly that this embodiment provided, including fixed gear support and fixed gear body, wherein, fixed gear support is both ends open-ended sleeve structure, and the convenience of drawing materials, processing are simple, are fit for mass production, and fixed gear body is direct to put into the mould as the inserts at fixed gear support, and both combine closely, and the uniformity of product is better. Meanwhile, the fixed gear support is made of metal materials and is directly welded with the valve seat body part in a laser welding mode, so that the fixed gear assembly is reliably positioned in the axial direction. It should be noted that, the fixed gear assembly provided in this embodiment is applicable to electric valve products with different structures, and the technical effects thereof do not depend on the valve seat structure, the slider structure, and the like described in the above embodiments.

Referring to fig. 7 and 8, fig. 7 is a schematic view of the front view of the gear slider according to the first embodiment of the present application, and fig. 8 is a schematic view of the back view of the gear slider according to the first embodiment of the present application. The gear slider 20 is generally in a bottomed cylinder shape, and includes a body portion 201 and a positioning portion 202 protruding from an outer edge portion of the body portion 201, the positioning portion 202 is generally in a sector ring shape in cross section and is disposed coaxially with the body portion 201, that is, an outer diameter of the positioning portion 202 is larger than an outer diameter of the body portion 201, so that the positioning portion 202 forms two end portions, that is, a first positioning portion 2021 and a second positioning portion 2022. The gear slider 20 further includes a through hole portion 204 provided at a central position thereof, and the valve shaft 14 is fixedly coupled to the valve seat assembly after passing through the through hole formed by the through hole portion 204, so that the gear slider 20 can rotate around the valve shaft 14. After the assembly, the gear slider 20 is coaxially disposed with the fixed gear 19, and the distance between the peripheral wall of the positioning portion 202 and the central axis matches the distance between the partition boss 1122 of the partition 112 and the central axis, that is, when the gear slider 20 rotates counterclockwise as shown to the limit position, the first positioning portion 2021 abuts against one side of the partition boss 1122, so that the gear slider cannot continue to rotate; when the gear slider 20 rotates clockwise as shown to the limit position, the second positioning portion 2022 abuts against the other side of the partition portion boss 1122, so that the gear slider cannot continue to rotate. Thus, the rotational travel of the gear slider is determined by the cooperation of the positioning portion 202 and the partition portion boss 1122. It should be noted that the length of the positioning portion 202 (i.e., the length along the circumferential direction of the gear slider) may be adjusted according to the system requirements.

The inner peripheral wall of the gear slider 20 is provided with a slider gear portion 203, and the slider gear portion 203 can be engaged with a planetary gear set described below and rotated by the drive of the planetary gear. The flow control portion 205 is provided at the bottom of the gear slider 20, the flow control portion 205 has a certain height as a whole, and as shown in fig. 7, the flow control portion 205 extends in the axial direction to a certain height on the bottom surface of the gear slider 20 to form a fitting surface 2051 for fitting with the fitting surface 1134 of the valve seat body portion 111 and being rotatable relative to the fitting surface 1134, and a notch portion 2052 is provided at one portion of the flow control portion 205, so that when the gear slider 20 is fitted to the valve seat body portion 111, the flow control portion 205 is located at the position of the notch portion 2052 without being in contact with the third plate portion 113, and fluid can flow in or out from a space formed by the notch portion 2052.

Referring to fig. 9, fig. 9 is a schematic diagram of a planetary gear set according to the first embodiment. The planetary gear set 18 includes a carrier 181 and a cover plate 182, the carrier 181 including a bottom 1812 and three support posts 1811 extending upwardly from the bottom 1812. In this embodiment, the configuration of 3 planetary gears is exemplified, and in practice, the configuration of the planetary gears may be set according to the output torque, and is not limited to 3 planetary gears. For this reason, in the present embodiment, the number of support columns 1811 is 3, and the distribution is uniform along the circumferential direction, and 3 planetary gears 183 are disposed between two adjacent support columns 1811. The planet carrier 181 is fixedly connected with the cover plate 182, and performs axial limiting on the planet gears 183. Specifically, apertures may be provided in cover 182 to allow for compression deformation of end 18111 of support post 1811 after it has been extended through the apertures, thereby achieving a secure connection. The planet carrier 181 may be formed by injection molding, and the cover plate 182 may be formed by stamping a metal plate, so that the end 18111 may be conveniently deformed by heating, so that the cover plate cannot be separated from the planet carrier. The 3 planetary gears 183 are respectively limited on the planetary carrier through the planetary gear shafts 184, and the planetary gears 183 can rotate around the planetary gear shafts 184, one end of each planetary gear shaft 184 is fixedly connected or limited and abutted with the bottom 1812 of the planetary carrier, and the other end is fixedly connected or abutted with the cover plate 182.

Taking one of the planetary gears 183 as an example, the planetary gears 183 include two-stage gears, i.e., a large diameter gear 1831 at an opposite upper end and a small diameter gear 1832 at an opposite lower end. The end surface of the large diameter gear 1831 side of the planetary gear 183 is provided with a plurality of relative position positioning holes 1833. During assembly, the sun gear 13 is inserted downwards from the central shaft of the planetary gear set 18 and meshed with the large-diameter gear 1831 to drive the planetary gears 183 to rotate, 3 planetary gears 183 enclose a virtual circle, the inner side of the large-diameter gear 1831 is meshed with the sun gear 13, and the outer side of the large-diameter gear 1831 is meshed with the fixed teeth 1912 of the fixed gear 19. In this way, when the sun gear 13 rotates, the planetary gear 183 is driven to rotate, and the planetary gear 183 rotates around the planetary gear shaft 184 and also rotates along the fixed teeth 1912 of the fixed gear. The small diameter gear 1832 is engaged with the slider gear 203 of the gear slider 20, so as to drive the gear slider 20 to rotate, and the rotation of the gear slider is stopped by the abutment of the first positioning portion 2021 and the second positioning portion 2022 with the protruding portions of the fixed gear, respectively, as described above. In this way, the motor-driven valve drives the rotor and the sun gear 13 to rotate through the electromagnetic coil, and the gear slider 20 is finally driven to rotate through the planetary gear set for deceleration, and the flow control part 205 arranged at the bottom of the gear slider is attached to the mating surface 1134 of the valve seat body 111, so that the notch 2052 of the flow control part corresponds to different parts of the flow regulating part 1116 of the third plate body, and the flow regulating function is realized.

Referring to FIG. 10, FIG. 10 is a schematic diagram illustrating an assembled planetary gear set according to one embodiment of the present application. In the present embodiment, the number of teeth of the sun gear is 12, and the number of teeth of the sun gear corresponds to 24 poles of the motor rotor, so that the product hardly generates phase deviation at the time of assembly. The fixed gears are provided with 48 fixed teeth, the number of teeth of the large diameter gear 1831 of the planetary gear set is 18, and the number of teeth of the small diameter gear 1832 is 12; correspondingly, the number of the positioning holes 1833 is 6, namely, the common divisor of 18 and 12. This design can achieve 1:21, i.e. a smaller planetary gear to output a larger gear ratio. The large diameter gear 1831 in the planetary gear is set to 18 teeth, and the small diameter gear is set to 12 teeth, so that the structural space of the output component can be miniaturized, the initial positioning space of the electric valve is relatively increased, the miniaturization of the electric valve is realized, the strength of the transmission gear at the output end can be increased, and the reliability of the product is improved. The positioning holes 1833 are used to determine the relative position and angle of the gears during assembly to facilitate the assembly operation. As shown in fig. 10, when assembling, the line passing through the three positioning holes 1833 of the three planetary gears to the midpoint of the planetary gear mechanism has an included angle of 120 degrees, so that the three planetary gears can be conveniently meshed with the fixed gear or the slider gear, and the positioning holes 1833 define the angles of the planetary gear teeth, so that the smooth meshing can be ensured when assembling, and the occurrence of interference can be reduced. The three planetary gears can be assembled with the fixed gear and then matched with the inner gear ring of the gear slide block through the determined gear tooth orientations after being positioned during assembly, and can also be assembled with the fixed gear after being matched with the inner gear ring of the gear slide block. The number of internal teeth of the slider gear portion may be set as necessary, and in the present embodiment, the number of teeth of the slider gear portion is 42.

The flow rate adjustment process is described below in connection with fig. 11-15. Fig. 11 is a schematic diagram of a positional relationship between the gear slider and the valve seat assembly when the electric valve is in a fully closed state, fig. 12 is a schematic diagram of a positional relationship between the gear slider and the valve seat assembly when the electric valve is in an intermediate state of flow regulation, and fig. 13 is a schematic diagram of a positional relationship between the gear slider and the valve seat assembly when the electric valve is in a fully open state. Fig. 14 is a schematic diagram of a refrigeration system, and fig. 15 is a flow chart of a refrigeration system.

As shown in fig. 14, a refrigeration system includes a compressor a01, an evaporator a02, a condenser a03, and an electrically operated valve a04, which constitute a basic refrigeration system circuit. Meanwhile, a filter A05 can be arranged in the loop to filter impurities in the refrigerating system, so that good operation of the system is ensured. In the refrigerating system, the electric valve replaces a capillary tube commonly used for throttling in a common refrigerator refrigerating system, so that the refrigerant flow of the refrigerating circuit can be adjusted, and when the electric valve is at a 10Ps (pulse) position, the flow is 0, and the electric valve is in a fully closed state as shown in fig. 15. Specifically, as shown in fig. 11, the second positioning portion 2022 of the gear slider 20 abuts against one side of the partition plate portion boss 1122, and at this time, in the projection view shown in fig. 11, the notched portion 2052 provided in the flow control portion 205 does not overlap with the flow rate adjustment portion 1116 and the valve port portion 1117 in the axial direction, that is, the flow rate adjustment portion 1116 and the valve port portion 1117 are both covered by the flow rate control portion 205, and fluid cannot flow into the flow rate adjustment portion 1116, and at this time, the electric valve is in the fully closed state. That is, there is at least one relative position between the gear slider 20 and the valve seat main body 111, and there is no overlap region between the projection of the notch 2052 in the axial direction and the projection of the valve port 1117 in the axial direction, and between the projection of the notch 2052 in the axial direction and the projection of the flow rate adjustment unit 1116 in the axial direction.

As shown in fig. 15, the electric valve is a linear flow rate adjustment region in the range of 50Ps to 500Ps, and controls the flow rate adjustment region range. Specifically, as shown in fig. 12, when the gear slider 20 rotates counterclockwise by a certain angle, the flow control portion 205 partially overlaps the flow adjustment portion 1116 in the projection in the axial direction, that is, a black region is shown as a part of the flow adjustment portion 1116, and at this time, the fluid in the valve chamber of the electric valve can flow in from the space formed by the notch portion 2052, flow into the arc-shaped groove formed by the flow adjustment portion 1116 through the black region of the flow adjustment portion 1116, and then flow out from the valve port portion 1117, and at this time, the cross-sectional area of the black region determines the throttle flow rate of the electric valve. It will be appreciated by those skilled in the art that fig. 12 shows a specific position of the gear slider, and the cross-sectional area of the corresponding black area will be increased as the gear slider 20 rotates, which is a flow rate adjusting process of the electric valve, and the flow rate adjusting interval is 0.25 to 10L/min, as shown in fig. 15. That is, at least one relative position is provided between the gear slider 20 and the valve seat main body 111, and the projection of the notch 2052 in the axial direction overlaps with the projection of the flow rate adjusting portion 1116 in the axial direction, so that the cross-sectional area of the overlap of the projections defines the flow rate of the electric valve. When the refrigerator is powered on initially, the evaporation temperature of the evaporator and the surface temperature of the evaporator are controlled to be in a condensation state by controlling the flow of the valve (0.25-10L/min), the air in the freezing chamber is driven by the fan to form convection through the evaporator, the refrigerator body is dehumidified for a set time, after the dehumidification, the output flow of the electric valve is regulated, the evaporation temperature of the evaporator and the surface temperature of the evaporator are controlled, the cooling of the refrigerator body is realized, after the dehumidification, the frosting and icing on the surface of the evaporator can be reduced and slowed down, the heat exchange efficiency is improved, and the quick cooling of the refrigerator and the energy consumption reduction are realized. For the air-cooled refrigerator, the temperature of the evaporator and the surface temperature of the evaporator can be adjusted to be in a condensation state by defrosting the evaporator, and the humidity of the refrigerating chamber of the air-cooled refrigerator can be increased and controlled by controlling the fan and the air door, so that the fresh-keeping effect of the air-cooled refrigerator is improved. For the direct-cooling refrigerator, a plurality of evaporators can be arranged in series, if necessary, each evaporator inlet is provided with an electric valve, or the evaporators are connected in parallel, and each evaporator inlet is provided with an electric valve.

As shown in FIG. 15, the electric valve is changed from the flow rate adjusting state to the full open state at 500Ps-650 Ps. The fully-opened flow is not less than 200L, and when the system operates in the state, the refrigerant path is as follows: compressor A01 exhaust port, condenser A04, filter A05, electric valve A04, evaporator A02 and compressor A01 air suction port. When the gear slider 20 rotates counterclockwise until the first positioning portion 2021 abuts against the other side of the partition plate boss 1122 as shown in fig. 13, the rotation is stopped, and at this time, the projection of the notch portion 2052 in the axial direction overlaps with the portion of the flow rate adjusting portion near the valve opening and the valve opening, that is, the valve opening 1117 is entirely located at the position of the notch portion 2052, and at this time, the fluid in the valve chamber of the electric valve flows in from the space formed by the notch portion 2052 and flows out from the valve opening 1117, as shown by the black area in fig. 13, and at this time, the electric valve is in the fully opened state. That is, at least one relative position exists between the gear slider 20 and the valve seat body 111, at least a partial projection of the notch 2052 in the axial direction overlaps with a projection of the valve port 1117 in the axial direction, the valve port formed by the valve port 1117 communicates with the internal space of the first adapter 114, and the inner diameter of the valve port 1117 defines the flow rate of the electric valve. In the integral operation state, the electric valve is fully opened and communicated with large flow, and is in a state of no throttling, but the gaseous cold coal circularly flows in the pipeline, and in the normal room temperature state, the temperature of the cold coal flowing into the evaporator is similar to the ambient temperature, and the cold coal exchanges with the outer surface of the evaporator of the freezing chamber, so that defrosting of the evaporator is realized.

The assembly process of the electric valve is described below. In one embodiment, the valve seat assembly may be assembled and fixed as one assembly, that is, the valve seat body portion 111 and the diaphragm portion 112 may be assembled and then fixed by welding. Or the valve seat body 111 is welded and fixed to the first connection pipe 114 and the second connection pipe 115, and then welded and fixed to the diaphragm 112. The valve shaft 14 may be fixedly connected to the valve seat assembly by welding or by press-fitting. Then, the gear slider is fitted, that is, the through hole 204 of the gear slider is fitted along the valve shaft 14, so that the fitting surface 2051 of the gear slider is fitted to the fitting surface 1134 of the valve seat. The planetary gear set 18 is then loaded into the gear slider 20 with the small diameter gear 1832 of the planetary gear set 18 meshed with the slider gear portion 203 and the large diameter gear 1831 located above the gear slider 20. The fixed gear 19 is then fitted from above, with the fixed teeth 1912 meshing with the outside of the large diameter gear 1831 of the planetary gear set. And then the fixed gear bracket 192 is welded to the valve seat body. Then, the rotor 12 with the sun gear 13, the spring 17 and the shaft sleeve 16 are arranged; the sleeve member is then installed.

Alternatively, another assembly method may be employed: the valve seat assembly is assembled and fixed as one assembly, that is, the valve seat body portion 111 and the diaphragm portion 112 are assembled and then fixed by welding. Or the valve seat body 111 is welded and fixed to the first connection pipe 114 and the second connection pipe 115, and then welded and fixed to the diaphragm 112. The valve shaft 14 may be fixedly connected to the valve seat assembly by welding or by press-fitting. Preparing a fixed gear assembly, and placing the fixed gear bracket as an insert into a mold to perform injection molding on a fixed gear body; assembling the planetary gear set to a fixed gear assembly, enabling the included angle between the connecting lines from one positioning hole of each of the three planetary gears to the midpoint of the planetary gear set to be 120 degrees by a positioning tool, and then meshing and assembling with the fixed gear assembly; assembling the gear slide block to the planetary gear set, and then assembling the fixed gear assembly, the planetary gear set and the gear slide block as a whole along the valve shaft, so that the joint surface of the gear slide block is jointed with the joint surface of the valve seat body part; the outer side of the large-diameter gear of the planetary gear set is meshed with the fixed gear; and (5) performing laser welding and fixing on the fixed gear support and the valve seat assembly. Then, the rotor 12 with the sun gear 13, the spring 17 and the shaft sleeve 16 are arranged; the sleeve member is then installed.

In the above two fitting methods, the first and second sleeve members may be prepared as described in the first embodiment, and then the sleeve members may be assembled by welding, or the sleeve members may be integrally press-molded. The sleeve member has a first side wall portion 1512, a second side wall portion 1522, a first top wall portion 1511, and a second top wall portion 1521, and after assembly, the second top wall portion 1521 is press-fitted with the upper end edge of the fixed gear 19 by interference fit, so as to axially position the fixed gear, and to weld and fix the sleeve member to the valve seat assembly.

The assembly sequence can also be correspondingly adjusted, for example, the gear slider and the planetary gear can be assembled first, and then the fixed gear bracket and the valve seat assembly are welded and fixed. That is, the above-described assembly process is merely an exemplary illustration of the assembly method of the electric valve provided in the present embodiment, and is not meant to limit the unique assembly sequence of the electric valve.

It should be noted that, in this embodiment, terms of up, down, left, right and other directions are all introduced for convenience of description with reference to the drawings in the specification; and the ordinal numbers "first," "second," etc., in the names of the components are also introduced for descriptive convenience and are not meant to imply any limitation on any order of the components. In the embodiments described in the present specification, various combinations of the embodiments of a certain member or component may be made with respect to each embodiment, and the present application is not limited to the technical features described in the embodiments, and any of the embodiments described above regarding the valve seat body portion may be combined with other embodiments regarding the fixed gear to form a new embodiment. While, at length, this specification does not describe each embodiment in any way as an example, it should be appreciated by those skilled in the art that any new embodiment of the application can be implemented without any inventive effort (e.g., by merely adapting the structure of the two components or parts to be combined, which is known in the art), and still fall within the scope of the claims.

The above describes the electrically operated valve provided by the present application in detail. The principles and embodiments of the present application have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the core concepts of the application. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the application can be made without departing from the principles of the application and these modifications and adaptations are intended to be within the scope of the application as defined in the following claims.

Claims

1. An electric valve is characterized by comprising a valve body (1), wherein the valve body (1) comprises a valve seat assembly (11), a sun gear (13), a fixed gear (19), a gear slider (20), a planetary gear set (18) and a valve shaft (14); the valve seat assembly (11) is fixedly connected or in limiting connection with the valve shaft (14), and the valve seat assembly (11) is fixedly connected with the sleeve part;

the planetary gear set (18) comprises at least three planetary gears (183), any one of the planetary gears (183) comprising a large diameter gear (1831) and a small diameter gear (1832); the gear slider (20) includes a slider gear portion (203), the slider gear portion (203) being meshed with the small diameter gear (1832);

the fixed gear (19) comprises a fixed gear body (191) and a fixed gear bracket (192), the fixed gear bracket (192) is made of a metal material, and the fixed gear bracket (192) and the valve seat assembly are welded and fixed;

the number of teeth of the fixed gears is 48, the number of teeth of the large-diameter gears is 18, and the number of teeth of the small-diameter gears is 12;

the end face of any one of the planetary gears (183) close to one side of the large-diameter gear is provided with a plurality of positioning holes, and the number of the positioning holes is a common divisor of the number of teeth of the large-diameter gear and the number of teeth of the small-diameter gear.

2. The electric valve according to claim 1, characterized in that the fixed gear bracket (192) is made of a stainless steel pipe, the fixed gear bracket (192) is provided with a bracket through hole portion (1921), and the fixed gear body (191) is fixedly connected with the fixed gear bracket (192) into an integral structure by injection molding, and fills the bracket through hole portion (1921).

3. The electric valve according to claim 2, wherein the fixed gear bracket (192) is sintered from a powder metallurgy material, and the fixed gear body (191) is injection molded from a polymer material.

4. A valve as claimed in any one of claims 1 to 3, wherein the gear slider (20) comprises a body portion (201) and a positioning portion (202), the outer diameter of the positioning portion is larger than the outer diameter of the body portion (201), a first positioning portion (2021) and a second positioning portion (2022) are formed at two ends of the positioning portion, the valve seat assembly comprises a partition plate portion, the partition plate portion comprises a partition plate portion boss (1122), the gear slider (20) can rotate around the valve shaft (14), when the gear slider (20) rotates to a limit position, the first positioning portion (2021) abuts against the partition plate portion boss (1122) to limit, and when the gear slider (20) rotates reversely to the limit position, the second positioning portion (2022) abuts against the partition plate portion boss (1122) to limit.

5. The electrically operated valve of claim 1 wherein the number of said locating holes is 6 and, in at least one position, one locating hole is present in each of said three planetary gear sets such that the line connecting each of said locating holes to the center point of said planetary gear set is at an angle of 120 degrees.

6. The electrically operated valve as set forth in claim 5, wherein said planetary gear set (18) includes a planet carrier (181) and a cover plate (182), said planet carrier (181) including a base (1812) and three support posts (1811) extending from said base, said planet carrier (181) being injection molded from plastic and said cover plate being stamped from sheet metal.

7. The electrically operated valve of claim 6, wherein said planetary gear set (18) includes a planetary gear shaft (184), said planetary gear (183) being restrained by said planetary gear shaft (184), and said planetary gear (183) being rotatable about said planetary gear shaft (184).

8. A valve according to any one of claims 1-3, characterized in that the number of teeth of said sun gear (13) is 12, said sun gear (13) being in mesh with the inner side of each of said planetary gears.

9. An electric valve according to any one of claims 1-3, characterized in that the valve seat assembly (11) comprises a valve seat body portion (111), the bottom of the gear slider (20) is provided with a flow control portion (205), the flow control portion (205) extends axially along the bottom surface of the gear slider (20) and is capable of being fitted to and rotatable relative to a mating surface of the valve seat body portion (111), and the flow control portion (205) is provided with a notch portion (2052).