CN110005833A

CN110005833A - Valve gear

Info

Publication number: CN110005833A
Application number: CN201810008020.1A
Authority: CN
Inventors: 不公告发明人
Original assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Current assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Priority date: 2018-01-04
Filing date: 2018-01-04
Publication date: 2019-07-12

Abstract

The invention discloses a kind of valve gear, including driving part and valve component, the valve component includes valve bottom plate, the first valve seat and the second valve seat, and first valve seat and second valve seat are fixed or be shaped in the valve bottom plate；First valve seat has the first interface being connected to valve chamber；The import is equipped with filtration members；It further include the valve block supported by second valve seat；Mutually matched flow adjusting structure is provided between second valve seat and the valve block, under the driving of the driving part, during the valve block can be rotated relative to second valve seat, and the valve block rotates, the flow adjusting structure can adjust cold medium flux size.The valve component split settings of the valve gear, it is easy to process, it can be ensured that the precision of flow adjusting structure makes valve gear have preferable flow consistency to improve flow accuracy.

Description

Valve device

Technical Field

The invention relates to the technical field of fluid control components, in particular to a valve device for flow regulation.

Background

Along with the improvement of energy efficiency requirements, a variable frequency refrigeration system mainly based on a variable frequency air conditioner develops rapidly, a capillary tube as a throttling element cannot meet the requirement of variable frequency of the refrigeration system, the capillary tube is replaced by various valves capable of adjusting flow, and at present, an electronic expansion valve is mainly used.

Referring to fig. 1, fig. 1 is a schematic cross-sectional view of a conventional electronic expansion valve.

When the valve is in use, the magnetic rotor 1 'of the motor is driven to rotate through the external magnet exciting coil to drive the valve needle screw rod 2' and the fixing nut 3 'to rotate relatively, so that the valve needle 5' at the valve port 4 'is moved up and down, and the change of the flow section of the valve port 4' is realized through the change of the relative position of the conical surface end part of the valve needle 5 'and the valve port 4', so that the flow rate is adjusted.

When the valve port 4 'is closed, in order to prevent the valve port 4' from locking with the valve needle 5 ', a spring 6' is arranged at the valve needle part, and the pressure difference of the inlet and the outlet is overcome through the spring force.

As above, the electronic expansion valve adjusts the flow rate by changing the relative position of the valve needle 5 'and the valve port 4', the change of the flow rate is related to the size of the valve port 4 'and the structure of the valve needle 5', the flow rate cannot be accurately controlled in practice, and the consistency of the flow rate is poor.

In addition, during the up-and-down movement of the valve needle 5 ', friction is inevitably generated between the valve needle 5' and the valve port 4 ', which affects the service life and performance of the electronic expansion valve (for example, internal leakage occurs), and meanwhile, when the valve needle 5' acts, friction between metals exists in related components, which not only generates friction noise, but also generates abrasion during oil-free lubrication, resulting in seizure, thereby affecting the normal function of the valve.

In view of this, how to design a valve device with good flow consistency is a technical problem that needs to be solved by those skilled in the art at present.

Disclosure of Invention

In order to solve the above technical problems, the present invention provides a valve device, comprising a driving component and a valve seat assembly, wherein the valve seat assembly comprises a valve bottom plate, a first valve seat and a second valve seat, and the first valve seat and the second valve seat are fixedly or integrally formed on the valve bottom plate; the first valve seat is provided with a first interface communicated with the valve cavity; the first interface is provided with a filter element;

further comprising a valve block supported by the second valve seat;

the flow regulating structure is arranged between the second valve seat and the valve block and matched with the second valve seat, the valve block can rotate relative to the second valve seat under the driving of the driving part, and in the rotating process of the valve block, the flow regulating structure can regulate the flow of a refrigerant.

The valve device provided by the invention abandons the valve needle structure of an electronic expansion valve in the prior art, arranges a component for adjusting the flow between the valve block and the second valve seat, and simultaneously improves the valve seat component correspondingly; specifically, the valve seat assembly comprises a valve bottom plate, a first valve seat and a second valve seat, a first interface communicated with the valve cavity is formed in the first valve seat, and a filter piece is arranged at the first interface, so that impurities can be prevented from entering the valve device; a flow regulating structure is arranged between the second valve seat and the valve block, the flow regulation is realized by the rotation of the valve block relative to the second valve seat, and the flow regulating structure is arranged between the valve block and the second valve seat, so that the precision control is convenient, and the better flow consistency can be obtained; meanwhile, each part of the valve seat assembly is separately processed, so that the processing of the second valve seat is facilitated, and the precision control of the flow regulating structure arranged on the valve seat assembly is facilitated.

In addition, the flow regulation of the valve device is realized by rotating the valve block relative to the second valve seat, the situation of clamping failure in the background technology cannot occur, the valve block and the second valve seat are sealed by a surface, the sealing performance can be improved, and therefore the reliability of the valve device is high.

The first valve seat is fixedly connected with a first connecting pipe, and the filtering piece is fixedly connected with the first valve seat or the first connecting pipe.

The first valve seat has a stepped through-hole facing downward, the stepped through-hole forming the first port; the first connecting pipe is fixedly embedded in the large-diameter hole of the stepped through hole; the filter element is provided with a folded edge which is bent outwards along the radial direction of the filter element, and the end part of the first connecting pipe presses the folded edge against the step surface.

And a second connecting pipe is fixedly connected with the second valve seat, and a silencing piece with a hole-shaped structure is arranged between the second connecting pipe and the second valve seat.

The second connecting pipe is fixedly connected into the outlet of the second valve seat, a protrusion extending downwards is arranged in the middle of the top wall of the valve of the second valve seat, and the silencing piece abuts between the second connecting pipe and the protrusion.

The valve bottom plate is a stamping part, and the first valve seat and the second valve seat are machined parts.

The top surface of the second valve seat is provided with more than two valve ports communicated with the second interfaces of the second valve seat, and the valve block is provided with a sealing part and a gap or a through hole communicated with the valve cavity; under the drive of the driving component, the valve block can rotate relative to the second valve seat, so that the sealing part closes all the valve ports, or the notch or the circulation hole is communicated with more than one valve port.

The flow areas of the valve ports are different, and the notches or the flow holes can be sequentially communicated with the valve ports in the rotating process of the valve block; or,

the flow areas of the valve ports are the same, and in the rotating process of the valve block, the notch or the flow hole can be communicated with one valve port or more than two valve ports.

The top surface of the second valve seat is provided with a valve port communicated with a second interface of the second valve seat, the valve block is provided with a sealing part and a runner groove which is circumferentially arranged around the rotation center of the valve block, and the runner groove is communicated with the valve cavity; the flow area of the runner groove is different along the circumferential direction of the runner groove;

under the drive of the driving component, the valve block can rotate relative to the second valve seat, so that the sealing part closes the valve port, or the runner groove is communicated with the valve port.

The valve block is provided with a flow hole or an opening communicated with the valve cavity, and the flow hole or the opening is positioned at one end of the runner groove and communicated with the runner groove; the radial widths of the runner grooves are the same; the axial depth of the flow channel groove gradually decreases from one end communicating with the circulation hole or the opening to the other end of the flow channel groove in the circumferential direction of the flow channel groove.

The driving part comprises a magnetic rotor and a rotating wheel fixedly connected with the magnetic rotor, and the rotating wheel is provided with external meshing teeth distributed along the circumferential direction; the valve block is provided with an outer gear part meshed with the outer meshing teeth, and the magnetic rotor can drive the rotating wheel to rotate so as to drive the valve block to rotate synchronously.

The second valve seat is fixedly connected with a rotating shaft, the rotating shaft is sleeved with the valve block, and the rotating shaft is further provided with a check ring to limit the axial position of the valve block relative to the rotating shaft.

The outer gear part of the valve block is provided with a section of continuous gear part used for limiting the rotation range of the valve block and the initial relative position of the valve block and the second valve seat.

Drawings

FIG. 1 is a schematic cross-sectional view of an electronic expansion valve of a conventional type;

FIG. 2 is a schematic cross-sectional view of one embodiment of a valve assembly according to the present invention;

FIG. 3 is a schematic illustration of the construction of the valve body components of the valve assembly of FIG. 2;

FIG. 4 is a schematic diagram of a coil assembly of the valve assembly of FIG. 2;

FIG. 5 is a cross-sectional view of the mounting portion of the valve body member and the coil member of FIG. 2;

FIG. 6 is a schematic diagram of a first mounting plate for the coil assembly in an exemplary embodiment;

FIG. 7 is a schematic diagram of the construction of a second mounting plate of the valve body assembly in an exemplary embodiment;

FIG. 8 is a schematic cross-sectional view of a valve body component in one embodiment;

FIG. 9 is a cross-sectional schematic view of the valve seat assembly of FIG. 8;

FIG. 10 is a top view of the second valve seat of FIG. 9;

FIG. 11 is a bottom view of one of the valve blocks of FIG. 8;

FIG. 12 is an enlarged fragmentary view of the valve block of FIG. 8 shown in engagement with the second valve seat;

FIG. 13 is a bottom view of the alternative valve block of FIG. 8;

FIG. 14 is a cross-sectional view of the valve block of FIG. 13 shown engaged with a second valve seat;

FIG. 15 is a top view of a second valve seat in another example embodiment;

FIG. 16 is a bottom view of a valve block engaged with the second valve seat of FIG. 15;

FIG. 17 is a cross-sectional view of the second valve seat of FIG. 15 in cooperation with the valve block of FIG. 16;

FIG. 18 is a bottom plan view of an alternative valve block that mates with the second valve seat of FIG. 15;

fig. 19 is a cross-sectional view of the second valve seat of fig. 15 in cooperation with the valve block of fig. 18.

Wherein, the one-to-one correspondence between component names and reference numbers in fig. 1 is as follows:

the magnetic rotor 1 ', the screw rod 2', the fixing nut 3 ', the valve port 4', the valve needle 5 'and the spring 6';

in fig. 2 to 19, the one-to-one correspondence between the component names and the reference numerals is as follows:

a coil component 100, a first mounting plate 101, a first bending section 111, a positioning convex part 112, a first guide section 113;

the valve body part 200, the second mounting plate 201, the second bending section 211, the positioning hole 212 and the second guide section 213;

a valve bottom plate 21, a first valve seat 22;

a second valve seat 23, a central hole 231, valve ports 232(232a, 232b, 232c, 232d, 232 e);

the valve block 24, the seal portion 241, the notch 242, the external gear portion 243, the tooth connecting portion 2431, and the first flow passage 244;

rotating shaft 25, retainer ring 26, central shaft 27, rotating wheel 28, magnetic rotor 29, shaft sleeve 30, shell 31, inlet pipe 32, outlet pipe 33, filtering piece 34 and silencing piece 35;

second valve seat 23 ', valve port 232';

the valve block 24 ', the sealing portion 241 ', the flow channel groove 242 ', the outer gear portion 243 ', the continuous tooth portion 2431 ', the second flow hole 244 ', and the opening 245 '.

Detailed Description

In order that those skilled in the art will better understand the disclosure, the invention will be described in further detail with reference to the accompanying drawings and specific embodiments.

It should be noted that the terms upper, lower and the like in the directional terms referred to herein are defined by the positions of the components in the drawings and the positions of the components relative to each other, are only used for the sake of clarity and convenience in describing the technical solutions, and should not be construed as absolutely limiting the scope of protection; similarly, "first", "second", etc. are used merely for convenience of description to distinguish different components having the same name, do not indicate an order, and are not to be construed as limiting.

Referring to fig. 2 to 4, fig. 2 is a schematic cross-sectional view of a valve device according to an embodiment of the present invention; FIG. 3 is a schematic illustration of the construction of the valve body components of the valve assembly of FIG. 2; fig. 4 is a schematic structural view of a coil member of the valve device of fig. 2.

In this embodiment, the valve device includes a coil component 100 and a valve body component 200, wherein the coil component 100 is sleeved outside the valve body component 200, and the coil component 100 is matched with the magnetic rotor 29 inside the housing 31 of the valve body component 200 to form a driving component, the specific function of which will be described later.

The valve apparatus is also provided with a mounting structure to fix the coil member 100 well to the valve body member 200.

In a specific embodiment, the mounting structure includes a first mounting plate 101 fixed to the bottom of the coil component 100 and a second mounting plate 201 fixed to the bottom of the valve body component 200, and specifically, the second mounting plate 201 is fixed to the bottom of the valve seat assembly of the valve body component 200.

Referring to fig. 5, fig. 5 is a cross-sectional view illustrating an installation portion of the valve body member and the coil member in fig. 2.

The first mounting plate 101 has a first bending section 111 extending toward the valve seat assembly, a positioning protrusion 112 is disposed on an inner side (a side close to the center of the valve device) of the first bending section 111, the second mounting plate 201 has a second bending section 211 extending toward the coil component 100, and the second bending section 211 has a positioning hole 212 engaged with the positioning protrusion 112. Specifically, the first bent section 111 protrudes downward in the axial direction, and the second bent section 211 protrudes upward in the axial direction, where the axial direction refers to the axial direction of the valve chamber R of the valve device.

The first mounting plate 101 and the second mounting plate 201 are both elastic members. The elastic member here means that the mounting plate can be quickly restored to the original state after being deformed by an external force and then the external force is cancelled. Of course, the elastic member should have a certain strength so that the valve body part 200 and the coil part 100 are reliably mounted.

During assembly, the coil component 100 is sleeved on the valve component 200 from top to bottom, so that the first bending section 111 corresponds to the second bending section 211, and in the illustrated embodiment, the first bending section 111 is located outside the second bending section 211; in the process of downward assembly, the positioning convex part 112 arranged at the inner side of the first bending section 111 can press the second bending section 211 inwards to generate certain elastic deformation, and correspondingly, the first bending section 111 can also generate certain elastic deformation under the action of the outwards pressing force; when the positioning protrusion 112 moves downward to the position of the positioning hole 212, the positioning protrusion is clamped into the positioning hole 212, at this time, the external force applied to the second bending section 211 by the positioning protrusion 112 disappears, the second bending section 211 rebounds outward, and the first bending section 111 rebounds inward, so that the positioning protrusion 112 and the positioning hole 212 can be tightly fitted, and the coil component 200 is prevented from coming off or shaking in the circumferential direction, thereby relatively fixing the coil component 100 and the valve component 200.

For more reliable fixation of the coil component 100 to the valve body component 200, the positioning boss 112 and the positioning hole 212 may be sized to have an interference fit.

Specifically, the positioning hole 212 is circular, and the shape of the positioning protrusion 112 is matched with the positioning hole 212. It is understood that the positioning hole 212 may have other shapes, such as an oval shape, or a square shape. The positioning hole 212 is designed to be relatively circular, so that the processing is convenient, and the assembly is convenient.

More specifically, on the basis that the positioning hole 212 is circular, the positioning protrusion 112 may be configured to have a conical structure, that is, the sectional area of the positioning protrusion 112 gradually increases from the inside to the outside, so that the assembly is facilitated. It will be appreciated that, so designed, the maximum outer diameter dimension of the locating boss 112 should coincide with the locating hole 212.

Referring to fig. 6 and 7, wherein fig. 6 is a schematic view of a first mounting plate of the coil assembly in an exemplary embodiment; fig. 7 is a schematic structural view of a second mounting plate of the valve body assembly in the example embodiment.

Further, the lower end of the first bending section 111 is inclined outwards to form a first guiding section 113, and the upper end of the second bending section 211 is inclined inwards to form a second guiding section 213.

Thus, during assembly, the first guiding segment 113 contacts the second guiding segment 213 first and moves downward with the second guiding segment 213, so as to facilitate the matching between the first bending segment 111 and the second bending segment 211.

Specifically, the first mounting plate 101 and the second mounting plate 201 can be stamping parts or injection molding parts, and the processing is simple and reliable.

It should be noted that, in actual installation, the first bending section 111 may also be located inside the second bending section 211, and at this time, the positioning protrusion 112 disposed on the first bending section 111 is located outside the first bending section 111. Accordingly, the first guide section at the lower end of the first bending section 111 is inclined inward, and the second guide section at the upper end of the second bending section 211 is inclined outward.

Referring to fig. 8 and 9 together, fig. 8 is a schematic cross-sectional view of a valve body component according to an embodiment; fig. 9 is a cross-sectional schematic view of the valve seat assembly of fig. 8.

In this embodiment, the valve body part 200 includes a valve seat assembly including a valve base plate 21, a first valve seat 22, and a second valve seat 23 which are separately provided; the valve bottom plate 21 is provided with mounting holes matched with the first valve seat 22 and the second valve seat 23, the first valve seat 22 and the second valve seat 23 are respectively and fixedly arranged in the corresponding mounting holes, and particularly, a welding fixing mode can be adopted, so that the valve bottom plate is simple, convenient and reliable.

Specifically, for positioning convenience, an upward step surface may be provided on the first valve seat 22 to abut against the bottom of the valve bottom plate 21, and an upward step surface may be provided on the second valve seat 23 to abut against the bottom of the valve bottom plate 21.

Of course, in actual installation, the outer diameters of the first valve seat 22 and the second valve seat 23 may also be arranged in an equal diameter manner, and a step surface for positioning is provided on the corresponding mounting hole to define the axial relative positions of the first valve seat 22 and the second valve seat 23 with respect to the valve bottom plate 21.

The valve bottom plate 21 is fixedly provided with a shell 31, as shown in the figure, the shell 31 is in a convex structure, a small-diameter section of the shell 31 is internally provided with a magnetic rotor 29, and a large-diameter section and the valve bottom plate 21 enclose to form a valve cavity R.

The first valve seat 22 has a first port communicating with the valve chamber R, and the second valve seat 23 has a second port; the following description will be given taking as an example a first port as an inlet and a second port as an outlet, that is, in this embodiment, the first valve seat 22 serves as an inlet valve seat and the second valve seat 23 serves as an outlet valve seat; it can be understood that, in practical application, the first valve seat 22 may also be used as an outlet valve seat, and the second valve seat 23 may also be used as an inlet valve seat, so that the first interface of the first valve seat 22 is an outlet of the refrigerant, and the second interface of the second valve seat 23 is an inlet of the refrigerant, and the principles of refrigerant flow adjustment are consistent, and will not be described again.

Specifically, a first connecting pipe is fixedly connected to the first valve seat 22, in this scheme, the first connecting pipe is a refrigerant inlet pipe, hereinafter referred to as an inlet pipe 32, and an inlet of the first valve seat 22 is communicated with the inlet pipe 32; a second connection pipe is fixed to the second valve seat 23, and in this embodiment, the second connection pipe is a refrigerant outlet pipe, and hereinafter, is referred to as an outlet pipe 33.

Valve body assembly 200 also includes a valve block 24 supported by a second valve seat 23.

Referring to fig. 10 to 12 together, fig. 10 is a top view of the second valve seat in fig. 9; FIG. 11 is a bottom view of one of the valve blocks of FIG. 8; fig. 12 is an enlarged view of a portion of the valve block of fig. 8 engaged with the second valve seat.

Wherein the top surface of the second valve seat 23 has more than two valve ports 232 for communicating with the outlet, and in the solution shown in fig. 10, the second valve seat 23 is exemplarily provided with five valve ports 232.

The valve block 24 has a seal portion 241 and a notch 242 communicating with the valve chamber R, and as shown in fig. 11, the notch 242 has a fan shape in the illustrated embodiment.

As will be understood from fig. 12, specifically, the bottom of the valve block 24 is provided with a circular convex portion extending downward in the axial direction, a fan-shaped notch 242 is formed in the convex portion, and a sealing portion 241 is formed on the bottom surface of the convex portion, and it is obvious that the sealing portion 241 of the valve block 24 is attached to the top surface of the second valve seat 23, so that a certain space is formed between the notch 242 and the second valve seat 23, and the space can communicate with the valve chamber R.

Under the driving of the driving component, the valve block 24 can rotate relative to the second valve seat 23, so that the sealing part 241 closes the valve port 232, or the notch 242 communicates with more than one valve port 232; specifically, the sealing portion 241 can close all the valve ports 232, so that the valve device is in a fully closed state.

As above, the valve device abandons the valve needle structure of the electronic expansion valve in the prior art, and realizes the components for adjusting the flow by mutually matching the valve block 24 and the improved second valve seat 23; specifically, more than two valve ports 232 communicating with the outlets are arranged on the top surface of the second valve seat 23, the valve block 24 is supported by the top surface of the second valve seat 23, the valve block 24 has a sealing portion 241 and a notch 242 communicating with the valve cavity R, and the valve block 24 can rotate relative to the second valve seat 23 by the driving of the driving part, so that the sealing portion 241 closes the valve ports 232 or the notch 242 communicates with the valve ports 232; as described above, the refrigerant flowing into the valve chamber R flows out through the valve port 232 communicating with the notch 242 of the valve block 24, the refrigerant flow rate is determined by the flow area of the valve port 232 communicating with the notch 242, and quantitative change of the flow rate can be achieved, and since the size accuracy of each valve port 232 provided in the second valve seat 23 can be controlled, the accuracy of the seal portion 241 and the notch 242 of the valve block 24 can be easily ensured, so that the flow rate adjustment accuracy can be ensured, and the flow rate uniformity is good.

In addition, the flow regulation of the valve device is realized by rotating the valve block 24 relative to the second valve seat 23, the situation of clamping failure cannot occur, the sealing performance can be improved by adopting surface sealing between the valve block and the second valve seat, and the reliability of the valve device is higher.

The valve seat assembly is of a split structure, so that the processing of each part is convenient, particularly the processing of each valve port 232 on the second valve seat 23 is convenient, and the control of the precision of each valve port 232 is facilitated.

It can be understood that, in actual installation, the valve seat assembly may also be an integrally formed structure.

In a specific embodiment, the flow areas of the valve ports 232 on the second valve seat 23 are different, as shown in fig. 10, and five valve ports 232 are 232a, 232b, 232c, 232d, and 232e in sequence along the counterclockwise direction from the perspective shown in fig. 10.

In the illustrated embodiment, the apertures of the five valve ports 232a, 232b, 232c, 232d, and 232e decrease in sequence, and the five valve ports 232a, 232b, 232c, 232d, and 232e are distributed on the same circumference with the rotation center of the valve block 24 as the center of circle.

After the design, in the rotation process of the valve block 24, the notches 242 are communicated with one valve port 232 at a time, and when the valve block 24 rotates along the same direction, the flow areas of the valve ports 232 communicated with the notches 242 sequentially increase or decrease progressively, which is convenient for flow adjustment in practical application.

Referring to fig. 8 and 12, when the refrigerant enters the valve chamber R from the inlet pipe 32, the refrigerant can flow into the valve port 232 communicating with the notch 242 from the notch 242 of the valve block 24, and flow out from the outlet pipe 33 through the valve port 232.

Arrows in fig. 12 indicate the flow direction of the refrigerant.

Furthermore, the corresponding central angles of the two adjacent valve ports 232 are equal, that is, the valve ports 232 are uniformly arranged on the circular arc section where the valve ports 232 are arranged; in this way, the valve block 24 facilitates the operation of the valve device by adjusting the flow rate once per rotation through the same angle.

It should be noted that, in practice, during the arrangement, the aperture of each valve port 232 may be irregular, and the valve ports 232 may also be unevenly arranged on the circular arc segment where the valve ports 232 are arranged. But are relatively, regularly and uniformly arranged as shown in fig. 10, which facilitates product control.

It should be further noted that, in actual installation, the plurality of valve ports 232 may not be distributed on the same circumference, and the sealing portion 241 and the notch 242 of the valve block 24 are adaptively adjusted according to the arrangement of the valve ports 232, as long as the sealing portion 241 can close all the valve ports 232 and the notch 242 can be sequentially communicated with each valve port 232 to adjust the flow rate change in the rotation process of the valve block 24 due to the cooperation of the two.

In a specific scheme, the valve block 24 can be made of engineering materials with high strength, is wear-resistant and small in friction coefficient, and can be suitable for oil-free environments.

In a specific scheme, referring to fig. 8, a central hole 231 is formed in the second valve seat 23, a rotating shaft 25 is disposed in the central hole 231, and specifically, the rotating shaft 25 and the second valve seat 23 can be fixed in a welding manner.

The valve block 24 is sleeved on the rotating shaft 25, and a retaining ring 26 is fixedly sleeved on the rotating shaft 25 to limit the axial position of the valve block 24 relative to the rotating shaft 25. That is, the valve block 24 is clamped between the retainer ring 26 and the second valve seat 23 to ensure that the valve block 24 can be closely attached to the top surface of the second valve seat 23 and the valve block 24 can rotate around the rotating shaft 25.

The design of the rotating shaft 25 can define the rotation center of the valve block 24 and prevent the valve block 24 from shifting during rotation.

Furthermore, in addition to the provision of the retainer ring 26, if the construction of the valve seat assembly permits, an elastic member may be provided between the top surface of the valve block 24 and the housing 31 to press the valve block 24 against the second valve seat 23.

The drive unit includes, in addition to the aforementioned coil unit 100 and the magnet rotor 29, a rotary wheel 28 fixedly connected to the magnet rotor 29, the rotary wheel 28 having external teeth distributed along the circumferential direction, and the valve block 24 having an external gear portion 243 engaged with the external teeth.

In operation, the magnetic rotor 29 is driven to rotate by the coil component 100, which drives the rotating wheel 28 to rotate, and the valve block 24 is driven to rotate by the meshing transmission of the external gear of the rotating wheel 28 and the external gear portion 243.

Specifically, the magnetic rotor 29 includes a cylindrical wall portion and a bottom wall portion, wherein the bottom wall portion has an insertion hole, the upper end of the rotating wheel 28 has an annular groove fitted with the insertion hole, and a limit structure is provided between the insertion hole and the annular groove to relatively fix the rotating wheel 28 and the magnetic rotor 29.

The limiting structure has multiple implementation modes, and a simpler mode is realized by the shapes of the jacks and the annular grooves. For example, the insertion hole is provided with at least one plane section, and the groove bottom of the annular groove is provided with a plane section matched with the plane section of the insertion hole, so that after the rotating wheel 28 is inserted into the magnetic rotor 29, the annular groove of the rotating wheel 28 is clamped in the insertion hole of the magnetic rotor 29, and the plane sections of the rotating wheel 28 and the magnetic rotor 29 are attached, so that the relative position of the rotating wheel 28 and the magnetic rotor 29 can be limited. Specifically, the insertion hole and the annular groove may be formed in a polygonal structure that fits each other.

The bottom wall portion of the magnet rotor 29 also has balance holes to keep the pressure balance of the upper and lower chambers of the magnet rotor 29.

Specifically, a central shaft 27 is inserted into the rotating wheel 28, one end of the central shaft 27 is fixedly inserted into the valve bottom plate 21, and the other end of the central shaft 27 is fixedly connected with the housing 31, so that the rotating center of the rotating wheel 28 can be limited, and the matching between the rotating wheel 28 and the valve block 24 can be ensured.

Referring to fig. 8, the other end of the central shaft 27 is fixedly connected to the housing 31 through a bushing 30, and specifically, a small preset distance is provided between the bottom end of the bushing 30 and the top end of the rotating wheel 28 to limit the play amplitude of the magnet rotor 29 in the axial direction.

In a specific embodiment, the external gear portion 243 of the valve block 24 further has a tooth connecting portion 2431 for limiting the rotation range of the valve block 24 and the initial relative position of the valve block 24 and the second valve seat 23, so as to facilitate the debugging of the product and the determination of the application time reference.

As shown in fig. 11, when the valve block 24 rotates to a position where the teeth connecting portion 2431 contacts the rotary wheel 28, the valve block 24 cannot be engaged with the external teeth of the rotary wheel 28 due to the teeth connecting structure of the teeth connecting portion 2431, and thus the valve block 24 can be stopped.

The toothed portion 2431 of the valve block 24 and the rotating wheel 28 may be configured to: when one end of the toothed portion 2431 contacts the rotating wheel 28, the sealing portion 241 of the valve block 24 closes all the valve ports 232, and the notches 242 can sequentially open the valve ports 232a, 232b, 232c, 232d and 232e in the rotating process of the valve block 24, so that the flow rate can be adjusted from high to low. Of course, the initial positions of the valve block 24 and the second valve seat 23 can be defined according to the requirement in practical application.

In a specific scheme, an inlet of the inlet pipe 32 is an inlet without throttling function, that is, the flow area of the inlet pipe is approximately equal to that of the inlet pipe 32, the throttling function is not performed on the refrigerant flowing into the valve cavity R, and the filter element 34 is arranged at the inlet to filter impurities in the refrigerant and prevent the impurities from entering the valve cavity R to block or wear related structural components.

Specifically, the filter element 34 is disposed between the first valve seat 22 and the inlet tube 32.

Referring to fig. 8, in particular, the first valve seat 22 has a stepped through hole facing downward, which is an inlet of the first valve seat 22; the outer diameter of the inlet pipe 32 is equivalent to the aperture of the large-diameter hole of the stepped through hole, the inlet pipe 32 is fixedly embedded in the large-diameter hole of the stepped through hole, the filter element 34 is provided with a folded edge which is bent outwards along the radial direction of the filter element, and the folded edge of the filter element 34 is pressed against the stepped surface of the stepped through hole by the upper end part of the inlet pipe 32; by designing in this way, the positioning of the filter element 34 is achieved by the cooperation of the inlet tube 32 and the first valve seat 22, the design of the fixing structure of the filter element 34 can be eliminated, and the implementation is simpler and more reliable. It can be understood that the stepped through hole with the downward stepped surface is composed of a large-diameter hole with a relatively large diameter and a small-diameter hole with a relatively small diameter, and the joint of the large-diameter hole and the small-diameter hole forms the stepped surface.

Of course, the filter element 34 can also be fixedly connected only to the first valve seat 22 or to the inlet tube 32.

In a specific embodiment, a muffler 35 is further provided between the second valve seat 23 and the outlet pipe 33, and it is needless to say that the muffler 35 has a hole-like structure to ensure the circulation of the refrigerant. The provision of the noise deadening member 35 can reduce noise.

Specifically, referring to fig. 8 and 12, the second valve seat 23 includes a valve top wall and a valve peripheral wall, wherein the valve port 232 is provided on the valve top wall; the middle part of the valve top wall of the second valve seat 23 is provided with a protrusion extending downwards, the outlet pipe 33 is embedded in the second valve seat 23, the silencing piece 35 is abutted between the outlet pipe 33 and the protrusion, the structure of fixing the silencing piece 35 is avoided, an annular cavity R1 is formed between the silencing piece 35 and the second valve seat 23, when the refrigerant flows out from the valve port 232, the refrigerant firstly passes through the annular cavity R1 and then flows out through the silencing piece 35, and the annular cavity R1 has a certain buffering effect on the refrigerant.

Wherein the valve base plate 21 of the valve seat assembly may be formed by punching, and the first valve seat 22 and the second valve seat 23 may be formed by machining.

Referring to fig. 13 and 14 together, fig. 13 is a bottom view of the alternative valve block of fig. 8; fig. 14 is a cross-sectional view of the valve block of fig. 13 in engagement with a second valve seat.

In this solution, the valve block 24 is similar in structure to the previous one, with the only difference that: the valve block 24 defines a first flow passage 244, rather than a notch 242, that communicates with the valve chamber R.

Referring to fig. 13 and 14, similarly, a circular projection projecting downward in the axial direction is provided on the bottom of the valve block 24, and a first flow through hole 244 penetrating the valve block 24 is opened at the position of the projection, and a seal portion 241 is formed on the bottom surface of the projection.

When the valve block 24 rotates relative to the second valve seat 23, the first through hole 244 can communicate with each valve port 232 in turn, and obviously, the position of the first through hole 244 should correspond to the position of the valve port 232.

For the convenience of structural design and processing, the valve ports 232 of the second valve seat 23 are preferably arranged on the same circumference with the rotation center of the valve block 24 as the center, so that the number and arrangement of the first through holes 244 on the valve block 24 are also determined conveniently.

Of course, the arrangement of the valve ports 232 of the second valve seat 23 may be designed to be changed according to actual needs, and the structures of the sealing portion 241 and the first flow hole 244 of the valve block 24 may be changed accordingly.

In a specific embodiment, the flow area of the first flow hole 244 of the valve block 24 is not smaller than the maximum flow area of the valve port 232, so that the refrigerant flow rate is completely determined by the size of the valve port 232, and the control is facilitated.

Referring to fig. 8 and 14, when the refrigerant enters the valve chamber R from the inlet pipe 32, the refrigerant can flow into the valve port 232 communicating with the first through hole 244 from the first through hole 244 of the valve block 24, and flow out from the outlet pipe 33 through the valve port 232.

Arrows in fig. 14 indicate the flow direction of the refrigerant.

In addition to the different arrangement of the flow areas of the valve ports 232, the flow areas of the valve ports 232 of the second valve seat 23 may also be arranged identically, and at this time, the structural design of the sealing portion 241, the notch 242 or the first flow through hole 244 of the valve block 24 is changed, so that the notch 242 or the first flow through hole 244 can communicate with one or more than two of the valve ports 232 during the rotation of the valve block 24, that is, the refrigerant flow rate is adjusted by changing the number of the communicated valve ports 232.

In each of the above solutions, the flow rate adjusting structure of the second valve seat 23 and the valve block 24 is provided in a manner that realizes quantitative change of the flow rate, and besides the design, the flow rate adjusting structure may be in other forms, so that the flow rate of the refrigerant can be continuously changed.

Referring to fig. 15-17, fig. 15 is a top view of a second valve seat in another embodiment; FIG. 16 is a bottom view of a valve block engaged with the second valve seat of FIG. 15; fig. 17 is a cross-sectional view of the second valve seat of fig. 15 in cooperation with the valve block of fig. 16.

In this embodiment, the other structures of the valve device are the same as those described above, and the description thereof will not be repeated.

In this embodiment, the second valve seat 23 ' is provided with only one valve port 232 ' communicating with the outlet, and the valve block 24 ' has a sealing portion 241 ' and a flow channel groove 242 ' circumferentially arranged around the rotation center of the valve block 24 ', and one end of the flow channel groove 242 ' communicates with the valve chamber R through the second flow hole 244 ', and it is apparent that the second flow hole 244 ' penetrates the valve block 24 ', and the flow channel groove 242 ' is provided at the bottom surface where the valve block 24 ' abuts against the second valve seat 23 '.

It should be noted that the second flow through hole 244 ' may not be disposed at one end of the flow channel 242 ', and in theory, the second flow through hole 244 ' may be disposed at any position of the flow channel 242 ', as long as the flow channel 242 ' can communicate with the valve chamber R through the second flow through hole, and in relative terms, the second flow through hole 244 ' is disposed at one end of the flow channel 242 ' and is convenient to process and control.

The flow area of the flow channel groove 242 'differs in the circumferential direction of the flow channel groove 242'.

The second valve seat 23 'and the valve block 24' are similar to those described above except for the structure for regulating the flow rate, for example, the valve block 24 'also has an outer gear portion 243' that is in meshing engagement with the outer gear teeth of the rotating wheel 28, and the outer gear portion 243 'also has a coupling tooth portion 2431' for stopping.

Wherein, the radial position of the runner groove 242 'corresponds to the radial position of the valve port 232' to ensure that the valve port 232 'can communicate with the runner groove 242'; it will be appreciated that, in this way, the portion of the circumferential region where the flow channel groove 242 ' is located where no groove or hole is provided forms the seal portion 241 ' for closing the valve port 232 '.

It can be understood that the maximum flow area of the second flow hole 244 ', the flow channel groove 242 ', and the valve port 232 ' are all related to the maximum refrigerant flow rate.

Specifically, the flow area of the second flow hole 244 ' may be not smaller than the maximum flow area of the flow channel 242 ', so as to ensure that the structure of the flow channel 242 ' plays a role in adjusting the flow rate of the refrigerant.

More specifically, the maximum flow area of the runner channel 242 'is not greater than the flow area of the valve port 232', so that the theoretical maximum achievable flow is determined by the valve port 232 ', the actual maximum flow is determined by the maximum flow area of the runner channel 242', and the actual flow of the product can be continuously adjusted between 0 and the actual maximum flow; for example, the flow rate which can be achieved by fully opening the valve port is 10, the flow rate which corresponds to the maximum flow area of the runner groove is 5, the product flow rate can be adjusted between 0 and 5, and the smaller the maximum flow rate is, the higher the adjustment precision is.

Of course, in practice, the relationship between the maximum flow areas of the second flow hole 244 ' and the flow channel slot 242 ' and the flow area of the valve port 232 ' may not be designed as described above.

For example, the maximum flow area of the runner channel 242 ' may be larger than the flow area of the valve port 232 ', so that the actual maximum flow is determined by the valve port 232 ', and the actual flow of the product may be continuously adjusted from 0 to the actual maximum flow; such as: the flow that the valve port 232 ' can reach is 10, the flow that runner groove 242 ' maximum flow area corresponds is 15, valve block 24 ' rotates to reach after certain position flow 10 because valve port 232 ' throttle, and the valve block 24 ' continues to rotate the in-process flow no longer changes, and the actual flow of product is adjusted between 0 to 10, and there is a section work interval to have the condition that the flow is 10 always.

The actual maximum flow rate is determined by the smaller of the maximum flow area of the runner channel 242 'and the flow area of the valve port 232'.

Referring to fig. 16, in this aspect, the flow channel grooves 242 'have the same radial width, and the flow channel grooves 242' have different axial depths in the circumferential direction; that is, both side wall portions of the flow channel groove 242 'are designed to have a circular arc line structure, and the change in the flow area of the flow channel groove 242' in the circumferential direction is realized by the change in the groove depth.

Specifically, in the circumferential direction of the flow channel groove 242 ', the axial depth of the flow channel groove 242' is gradually reduced from one end communicating with the second flow through hole 244 'toward the other end of the flow channel groove 242', that is, the second flow through hole 244 'is arranged at the end of the flow channel groove 242' where the flow area is largest; therefore, in the process that the valve block 24' rotates towards the same direction, the flow of the refrigerant is gradually increased or decreased, and the operation in practice is convenient.

More specifically, the axial depth of the runner groove 242' is uniformly increased in the axial direction to improve the accuracy and uniformity of flow control.

Referring to fig. 8 and 17, when the refrigerant flows into the valve chamber R from the inlet pipe 32, the refrigerant flows into the channel groove 242 ' from the second flow hole 244 ' of the valve block 24 ' and flows out of the outlet pipe 33 through the valve port 232 ' communicating with the channel groove 242 '.

In this embodiment, the change in the flow rate is controlled by the change in the flow area of the channel groove 242', and the continuous change in the refrigerant flow rate can be realized.

Referring to fig. 18 and 19 together, fig. 18 is a bottom view of an alternative valve block that cooperates with the second valve seat of fig. 15; fig. 19 is a cross-sectional view of the second valve seat of fig. 15 in cooperation with the valve block of fig. 18.

In this solution, the valve block 24' is structurally similar to the above solution, with the only difference that: the valve block 24 'is provided with an opening 245' communicating with the valve chamber R, and the flow passage groove 242 'communicates with the valve chamber R through the opening 245'.

The structural design of the runner channel 242 'of the valve block 24' remains consistent with the above-described arrangement.

Specifically, the opening 245 'is designed to have a flow area not smaller than the maximum flow area of the flow channel groove 242', and the opening 245 'is provided at the end of the flow channel groove 242' where the flow area is largest. The maximum flow area of the runner channel 242 'is also preferably no greater than the flow area design of the valve port 232'.

Referring to fig. 8 and 19, when the refrigerant flows into the valve chamber R from the inlet pipe 32, the refrigerant flows into the channel groove 242 ' from the opening 245 ' of the valve block 24 ' and flows out of the outlet pipe 33 through the valve port 232 ' communicating with the channel groove 242 '.

In the above-mentioned embodiments, the flow area of the flow channel 242 ' is determined by the depth of the channel, and it is understood that the flow channel 242 ' may be configured in other ways in practice, for example, by changing the radial width of the flow channel 242 ' to change the flow area, or by changing the radial width in combination with the depth of the channel, i.e., the axial depth.

The valve device provided by the present invention is described in detail above. The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the method and its core concepts. It should be noted that, for those skilled in the art, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.

Claims

1. The valve device comprises a driving component and a valve seat assembly, and is characterized in that the valve seat assembly comprises a valve bottom plate (21), a first valve seat (22) and a second valve seat (23, 23 '), wherein the first valve seat (22) and the second valve seat (23, 23') are fixedly arranged on or integrally formed with the valve bottom plate (21); the first valve seat (22) has a first interface communicating with the valve chamber (R); the first interface is provided with a filter element (34);

further comprising a valve block (24, 24 ') supported by said second valve seat (23, 23');

a flow regulating structure which is matched with each other is arranged between the second valve seat (23, 23 ') and the valve block (24, 24 '), the valve block (24, 24 ') can rotate relative to the second valve seat (23, 23 ') under the driving of the driving part, and the flow regulating structure can regulate the flow of the refrigerant in the process of rotating the valve block (24, 24 ').

2. Valve device according to claim 1, characterized in that a first connecting piece is fastened to the first valve seat (22), and the filter element (34) is fixedly connected to the first valve seat (22) or the first connecting piece.

3. A valve device according to claim 2, characterized in that the first valve seat (22) has a stepped through hole facing downwards, which forms the first interface; the first connecting pipe is fixedly embedded in the large-diameter hole of the stepped through hole; the filter element (34) is provided with a folded edge which is bent outwards along the radial direction of the filter element, and the end part of the first connecting pipe presses the folded edge against the step surface.

4. A valve device according to claim 1, characterized in that a second connecting pipe is fixed to the second valve seat (23, 23 '), and a sound-absorbing member (35) having a hole-like structure is provided between the second connecting pipe and the second valve seat (23, 23').

5. A valve device according to claim 4, characterized in that the second nipple is fixedly connected in the outlet of the second valve seat (23, 23 '), the middle of the valve top wall of the second valve seat (23, 23') having a downwardly extending projection, the sound deadening member (35) abutting between the second nipple and the projection.

6. The valve device according to any one of claims 1 to 5, characterized in that the valve base plate (21) is a stamped part and the first valve seat (22) and the second valve seat (23, 23') are both machined parts.

7. The valve device according to any one of claims 1 to 5, wherein the top surface of the second valve seat (23) has two or more valve ports (232) communicating with the second port thereof, and the valve block (24) has a sealing portion (241) and a gap (242) or a flow hole communicating with the valve chamber (R); under the drive of the driving component, the valve block (24) can rotate relative to the second valve seat (23) so that the sealing part (241) closes all the valve ports (232) or the notch (242) or the through hole is communicated with more than one valve port (232).

8. The valve device according to claim 7, characterized in that the flow area of each valve port (232) is different, and the gap (242) or the flow hole can be communicated with each valve port (232) in turn during the rotation of the valve block (24); or,

the flow areas of the valve ports (232) are the same, and in the rotating process of the valve block (24), the notch (242) or the flow hole can be communicated with one valve port (232) or more than two valve ports (232).

9. The valve device according to any one of claims 1 to 5, wherein the top surface of the second valve seat (23 ') has a valve port (232 ') communicating with the second port thereof, the valve block (24 ') has a seal portion (241 ') and a flow channel groove (242 ') circumferentially arranged around the rotational center of the valve block (24 '), the flow channel groove (242 ') communicating with the valve chamber (R); the flow area of the flow channel groove (242 ') is different in the circumferential direction of the flow channel groove (242');

under the driving of the driving component, the valve block (24 ') can rotate relative to the second valve seat (23') so that the sealing part (241 ') closes the valve port (232') or the runner groove (242 ') is communicated with the valve port (232').

10. The valve device according to claim 9, characterized in that the valve block (24 ') has a flow hole or opening (245 ') communicating with the valve chamber (R), the flow hole or opening (245 ') being located at one end of the runner channel (242 ') and communicating with the runner channel (242 '); the radial widths of the runner grooves (242') are the same; the axial depth of the flow channel groove (242 ') gradually decreases from one end communicating with the flow hole or the opening (245') to the other end of the flow channel groove (242 ') in the circumferential direction of the flow channel groove (242').

11. A valve device according to any one of claims 1 to 5, characterized in that said drive means comprise a magnetic rotor (29) and a rotating wheel (28) fixedly connected to said magnetic rotor (29), said rotating wheel (28) having circumferentially distributed external toothing; the valve block (24, 24 ') is provided with an outer gear part (243, 243 ') meshed with the outer gear teeth, and the magnetic rotor (29) can drive the rotating wheel (28) to rotate so as to drive the valve block (24, 24 ') to rotate synchronously.

12. The valve device according to claim 11, wherein a rotating shaft (25) is fixedly connected to the second valve seat (23, 23 '), the valve block (24, 24 ') is sleeved on the rotating shaft (25), and a retaining ring (26) is further arranged on the rotating shaft (25) to limit the axial position of the valve block (24, 24 ') relative to the rotating shaft (25).

13. Valve arrangement according to claim 11, characterized in that the outer gear portion (243, 243 ') of the valve block (24, 24') has a length of a toothed portion (2431, 2431 ') for limiting the range of rotation of the valve block (24, 24') and the initial relative position of the valve block (24, 24 ') and the second valve seat (23, 23').