CN218543194U - Throttling valve and refrigerating system with same - Google Patents

Abstract

The utility model provides a choke valve and have its refrigerating system. The throttle valve includes: the valve seat is provided with a mounting cavity and a valve port communicated with the mounting cavity, at least part of cavity wall of the mounting cavity forms a first reference surface S1, and the valve port is arranged on the first reference surface S1; the valve needle comprises a body section and an adjusting section, the body section is arranged in the mounting cavity in a penetrating mode, the adjusting section is arranged in the valve port in a penetrating mode, and the adjusting section moves under the pushing of a medium entering the valve port to adjust the opening degree of the valve port; the peripheral surface of the end of the body section connected with the adjusting section is a conical surface; the valve port forms a datum line on the first datum plane S1, and a second datum plane S2 perpendicular to the first datum plane S1 is formed by passing through the datum line; when the throttle valve is in a closed state, a first preset distance h1 is reserved between the intersection line of the second reference surface S2 and the conical surface and the reference line, a gap is reserved between the valve port and the adjusting section, and the first preset distance h1 is larger than or equal to 0.3mm and smaller than or equal to 0.4mm. The utility model provides a problem that the throttle valve easily produced the noise when refrigerating system starts among the prior art.

Description

Throttle valve and refrigerating system with same

Technical Field

The utility model relates to a choke valve technical field particularly, relates to a choke valve and have its refrigerating system.

Background

At present, a throttle valve is applied in a refrigeration system to adjust a flow rate or a flow velocity of a refrigerant.

However, in the prior art, when the refrigeration system is started, the throttle valve generates a severe squeaking sound for about 10s, which not only causes the unqualified detection of the noise perceived by the ear of the refrigeration system, but also affects the use experience of the user.

SUMMERY OF THE UTILITY MODEL

The utility model discloses a main aim at provides a choke valve and have its refrigerating system to the problem of choke valve easily production noise when refrigerating system starts among the solution prior art.

In order to achieve the above object, according to an aspect of the present invention, there is provided a throttle valve, including: the valve seat is provided with a mounting cavity and a valve port communicated with the mounting cavity, at least part of cavity wall of the mounting cavity forms a first reference surface S1, and the valve port is arranged on the first reference surface S1; the valve needle is movably arranged in the valve seat; the valve needle comprises a body section and an adjusting section connected with the body section, the body section is arranged in the mounting cavity in a penetrating manner, the adjusting section is arranged in the valve port in a penetrating manner, and the adjusting section moves in a reciprocating manner under the pushing of a medium entering the valve port so as to adjust the opening degree of the valve port; the outer peripheral surface of one end of the body section, which is connected with the adjusting section, is a conical surface, and the size of the conical surface is gradually increased along the direction from the adjusting section to the body section; the valve port forms a datum line on the first datum plane S1, and a second datum plane S2 perpendicular to the first datum plane S1 is formed by passing through the datum line; when the throttle valve is in a closed state, a first preset distance h1 is reserved between the intersecting line of the second reference surface S2 and the conical surface and the reference line, a gap is reserved between the valve port and at least part of the adjusting section, and the first preset distance h1 is larger than or equal to 0.3mm and smaller than or equal to 0.4mm.

Use the technical scheme of the utility model, when the choke valve is in the closed condition, have first preset distance h1 between second reference surface S2 and the intersect line and the datum line of toper face to make have the clearance between valve port and the at least partial adjustment section, be similar to flow design when totally closed. Therefore, when the refrigerating system is started, part of the medium can enter the installation cavity through the gap before the medium pushes the valve needle to move, and the phenomenon that the front pressure and the rear pressure of the valve port are increased sharply to increase the friction force between the medium and the throttle valve is avoided until the medium can push the valve needle to move and throttle the medium.

Compared with the design that the throttle valve is not provided with flow when being fully closed in the prior art, the throttle valve has the flow design when being fully closed, on one hand, the pressure at the valve port is reduced, on the other hand, the pressure in the front and the back of the valve port is prevented from being sharply increased, the friction force between a medium and the throttle valve is reduced, the problem that the throttle valve is prone to generating noise when a refrigeration system is started in the prior art is solved, the noise when the refrigeration system is started is reduced, and the use experience of a user is improved.

Further, the shape of the adjustment segment, the internal pressure difference of the throttle valve and the diameter of the valve port are set so that the flow curve of the throttle valve has the following characteristics: the flow curve comprises a starting point A ', a first turning point B ' and an end point, wherein the starting point A ' corresponds to the closing state of the throttle valve, the flow of the valve port at the starting point A ' is Q0, the flow of the valve port at the first turning point B ' is Q1, the end point corresponds to the full-opening state of the throttle valve, the flow of the valve port at the end point is Q2, and the conditions that Q0 is more than 0 and Q1 is more than Q2 are met.

Further, the adjusting section includes: a first column section; the body section is connected with the second column section through the first column section, and a first ridge line L1 is formed at the joint of the first column section and the second column section; when the valve needle moves until the first ridge line L1 is in the first reference surface S1, a second preset distance h2 is reserved between the reference line and the intersection line of the second reference surface S2 and the conical surface, and the second preset distance h2 is larger than or equal to 1.05mm and smaller than or equal to 1.85mm.

Furthermore, the end part of the second column section, which is far away from the first column section, is an arc-shaped surface, and the flow curve also comprises an arc-shaped line section positioned between the first turning point B 'and the end point E'; wherein the second preset distance h2 is greater than or equal to 1.75mm and less than or equal to 1.85mm.

Further, when the valve needle moves to the full-open state, a third preset distance h3 is formed between the reference line and the intersection line of the second reference surface S2 and the conical surface, and the third preset distance h3 is greater than or equal to 2.35mm and smaller than or equal to 2.45mm.

Further, the adjusting section further comprises: the conical section is connected with one end, far away from the first column section, of the second column section, a second ridge line L2 is formed at the connection position of the second column section and the conical section, and the flow curve further comprises a second turning point C 'located between the first turning point B' and the end point; when the valve needle moves until the second ridge line L2 is in the first reference surface S1, a fourth preset distance h4 is reserved between the reference line and the intersection line of the second reference surface S2 and the conical surface, and the fourth preset distance h4 is greater than or equal to 1.35mm and smaller than or equal to 1.45mm; the first preset distance h1 is more than or equal to 0.3mm and less than or equal to 0.4mm; the second preset distance h2 and the fourth preset distance h4 satisfy the following condition: h4-h2 is less than or equal to 0.2mm; or the flow rate of the valve port at the second turning point C' is Q3, and the conditions that Q1/Q3 is more than or equal to 0.3 and less than or equal to 0.5 are met, and the fourth preset distance h4 and the second preset distance h2 meet the following conditions: h4-h2 is less than or equal to 0.5mm.

Further, the outer peripheral face of second cylinder section is the conical surface, and the adjustment section still includes: the third column section is connected with one end, far away from the second column section, of the conical section, a third ridge line L3 is formed at the connecting position of the third column section and the conical section, and the flow curve further comprises a third turning point located between the second turning point and the end point; when the valve needle moves to the third edge line L3 in the first reference surface S1, a fifth preset distance h5 is reserved between the reference line and the intersection line of the second reference surface S2 and the conical surface, the fifth preset distance h5 is greater than or equal to 1.75mm and smaller than or equal to 1.85mm, and the fifth preset distance h5 and the fourth preset distance h4 meet the following requirements: h5-h4 is more than or equal to 0.4mm and less than or equal to 0.5mm; the flow of the valve port at the third turning point is Q4, and the Q1/Q4 is more than or equal to 0.4 and less than or equal to 0.7.

Furthermore, the valve seat is also provided with a medium inlet which is communicated with the mounting cavity through a valve port; the medium inlet is in a horn shape, and the size of the medium inlet is gradually reduced along the direction from the medium inlet to the mounting cavity.

Further, the medium inlet is trumpet-shaped, and the corresponding central angle theta meets the following requirements: theta is more than or equal to 15 degrees and less than or equal to 90 degrees.

According to the utility model discloses a further aspect provides a refrigerating system, including foretell choke valve, refrigerating system's rated refrigeration capacity C more than or equal to 2.5KW and less than or equal to 7.5KW.

Drawings

The accompanying drawings, which form a part of the specification, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate exemplary embodiments of the invention and together with the description serve to explain the invention and do not constitute a limitation on the scope of the invention. In the drawings:

fig. 1 shows a perspective cross-sectional view of a first embodiment of a throttle valve according to the present invention;

FIG. 2 shows a cross-sectional view of the throttle valve of FIG. 1;

FIG. 3 is a cross-sectional view of the valve needle of the throttle valve of FIG. 1 assembled with the valve seat, spring and plug;

FIG. 4 shows a partial cross-sectional view of the valve needle of FIG. 3 assembled with a valve seat, spring and plug;

FIG. 5 shows a partial cross-sectional view of the valve seat of FIG. 3;

FIG. 6 shows a schematic perspective view of the valve needle of the throttle valve of FIG. 1;

FIG. 7 shows a cross-sectional view of the throttle valve of FIG. 1 in a closed state;

FIG. 8 shows a cross-sectional view of the section A-B of the valve needle of the throttle valve of FIG. 7 as positioned within the valve orifice;

FIG. 9 shows a cross-sectional view of section B-C of the valve needle of the throttle valve of FIG. 7 as positioned within the valve orifice;

FIG. 10 shows a cross-sectional view of the valve needle of the throttle valve of FIG. 7 with section C-D located within the valve port;

FIG. 11 shows a flow curve for the throttle valve of FIG. 1 with a valve port diameter of 1.0 mm;

FIG. 12 shows a flow curve for the throttle valve of FIG. 1 with a valve port diameter of 1.2 mm;

FIG. 13 shows a flow diagram for the throttle valve of FIG. 1 with a valve port diameter of 1.3 mm;

FIG. 14 shows a flow diagram for the throttle valve of FIG. 1 with a valve port diameter of 1.5 mm;

FIG. 15 shows a flow curve for the throttle valve of FIG. 1 with a valve port diameter of 1.7 mm;

figure 16 shows a cross-sectional view of a throttle valve according to a second embodiment of the throttle valve of the present invention in a closed state;

FIG. 17 shows a cross-sectional view of the valve needle of the throttle valve of FIG. 16 with section A-B located within the valve port;

FIG. 18 shows a cross-sectional view of section B-C of the valve needle of the throttle valve of FIG. 16 positioned within the valve orifice;

FIG. 19 is a graph showing the flow rate at 1.0mm of valve port diameter for the throttle valve of FIG. 16;

FIG. 20 is a graph showing the flow rate profile of the throttle valve of FIG. 16 with a valve port diameter of 1.2 mm;

FIG. 21 is a graph showing the flow rate at 1.3mm port diameter for the throttle valve of FIG. 16;

FIG. 22 is a graph showing the flow rate at 1.5mm of valve port diameter for the throttle valve of FIG. 16;

FIG. 23 is a graph showing the flow rate at 1.7mm of valve port diameter for the throttle valve of FIG. 16;

figure 24 shows a cross-sectional view of a third embodiment of a throttle valve according to the present invention in a closed state;

FIG. 25 shows a cross-sectional view of the section A-B of the valve needle of the throttle valve of FIG. 24 as positioned within the valve orifice;

FIG. 26 shows a cross-sectional view of the section C-D of the valve needle of the throttle valve of FIG. 24 positioned within the valve orifice;

FIG. 27 shows a cross-sectional view of the throttle valve of FIG. 24 with section D-E of the valve needle positioned within the valve port

FIG. 28 shows a flow rate profile for the throttle valve of FIG. 24 with a valve port diameter of 1.0 mm;

FIG. 29 is a graph showing the flow rate at 1.2mm of valve port diameter for the throttle valve of FIG. 24;

FIG. 30 is a graph showing the flow rate profile of the throttle valve of FIG. 24 with a valve port diameter of 1.3 mm;

FIG. 31 is a graph showing the flow rate at 1.5mm of valve port diameter for the throttle valve of FIG. 24;

fig. 32 shows a flow rate profile for the throttle valve of fig. 24 with a valve port diameter of 1.7 mm.

Wherein the figures include the following reference numerals:

10. a valve seat; 11. a mounting cavity; 12. a valve port; 13. a media inlet; 20. a valve needle; 21. a body section; 22. an adjustment section; 221. A first column section; 222. a second column section; 223. a conical section; 224. a third column section; 30. a screen assembly; 40. a plug; 50. A spring.

Detailed Description

It should be noted that, in the present application, the embodiments and features of the embodiments may be combined with each other without conflict. The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.

It is to be noted that, unless otherwise indicated, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs.

In the present invention, unless otherwise specified, the use of directional words such as "upper and lower" is generally in reference to the orientation shown in the drawings, or to the vertical, perpendicular or gravitational orientation; likewise, for ease of understanding and description, "left and right" are generally to the left and right as shown in the drawings; the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself, but the above directional terms are not intended to limit the present invention.

In order to solve the problem that a throttle valve is prone to generating noise when a refrigerating system is started in the prior art, the application provides the throttle valve and the refrigerating system with the same.

Example one

As shown in fig. 1 to 15, the throttle valve includes a valve seat 10 and a valve needle 20. The valve seat 10 has a mounting cavity 11 and a valve port 12 communicating with the mounting cavity 11, at least part of the cavity wall of the mounting cavity 11 forms a first reference surface S1, and the valve port 12 is on the first reference surface S1. A valve needle 20 is movably arranged in the valve seat 10; the valve needle 20 comprises a body section 21 and an adjusting section 22 connected with the body section 21, the body section 21 is arranged in the mounting cavity 11 in a penetrating manner, the adjusting section 22 is arranged in the valve port 12 in a penetrating manner, and the adjusting section 22 reciprocates under the pushing of a medium entering the valve port 12 to adjust the opening degree of the valve port 12. The outer peripheral face of this body section 21 and the one end of adjusting the section 22 and being connected is the conical surface, and along adjusting the section 22 to the direction of body section 21, the size of conical surface increases gradually. The valve port 12 forms a reference line on the first reference surface S1, and a second reference surface S2 perpendicular to the first reference surface S1 is formed by crossing the reference line; when the throttle valve is in a closed state, a first preset distance h1 is reserved between the intersecting line of the second reference surface S2 and the conical surface and the reference line, a gap is reserved between the valve port 12 and at least part of the adjusting section 22, and the first preset distance h1 is greater than or equal to 0.3mm and less than or equal to 0.4mm.

By applying the technical solution of the present embodiment, when the throttle valve is in the closed state, a first preset distance h1 is provided between the reference line and the intersection line of the second reference surface S2 and the conical surface, so that a gap is provided between the valve port 12 and at least a part of the adjusting section 22, which is similar to a full-closed flow design. Therefore, when the refrigeration system is started, before the medium pushes the valve needle 20 to move, part of the medium can enter the mounting cavity 11 through the gap, and the phenomenon that the pressure in the front and the back of the valve port 12 is increased sharply to increase the friction force between the medium and the throttle valve is avoided until the medium can push the valve needle 20 to move and throttle the medium.

Compared with the design of no flow when the throttle valve is fully closed in the prior art, the throttle valve in the embodiment has the flow design when the throttle valve is fully closed, so that the pressure at the valve port 12 is reduced, the rapid increase of the pressure in the front and the back of the valve port 12 is avoided, the friction between a medium and the throttle valve is reduced, the problem that the throttle valve is easy to generate noise when a refrigeration system is started in the prior art is solved, the noise when the refrigeration system is started is reduced, and the use experience of a user is improved.

Compared with the throttle valve in the prior art, the throttle valve in the embodiment has no part increase, and further has no cost increase.

The opening degree of the valve port is a valve needle opening degree, and is a value indicating the opening degree of the valve needle. Wherein the preset distance represents an opening value of the valve needle.

In the present embodiment, the shape of the adjustment segment 22, the internal pressure difference of the throttle valve, and the diameter of the valve port 12 are set such that the flow curve of the throttle valve has the following characteristics: the flow curve includes a starting point a ', a first turning point B ' and an end point, the starting point a ' corresponds to the closed state of the throttle valve, the flow rate of the valve port 12 at the starting point a ' is Q0, the flow rate of the valve port 12 at the first turning point B ' is Q1, the end point corresponds to the full open state of the throttle valve, the flow rate of the valve port 12 at the end point is Q2, and Q0 < Q1 < Q2 are satisfied. Therefore, in the operation process of the throttling valve, along with the change of the valve pressure difference, the flow is influenced along with the change of the pressure difference and the flow area, and the whole flow is of a broken line type, so that the flow of the throttling valve is gradually increased, and the phenomenon that the noise is generated and the use experience of a user is influenced due to the influence of sudden increase and sudden decrease of the flow of the throttling valve is avoided.

As shown in fig. 3, 4, and 6 to 10, the adjustment section 22 includes a first column section 221 and a second column section 222. The body section 21 is connected to the second column section 222 through the first column section 221, and a first ridge L1 is formed at a joint of the first column section 221 and the second column section 222. When the valve needle 20 moves until the first ridge L1 is in the first reference surface S1, a second preset distance h2 is formed between the reference line and an intersection line of the second reference surface S2 and the conical surface, and the second preset distance h2 is greater than or equal to 1.05mm and less than or equal to 1.25mm. Thus, the first column section 221 is a cylindrical section, the end of the second column section 222 connected with the first column section 221 is consistent with the outer diameter of the first column section 221, the flow area of the first column section 221 is unchanged in the process of moving in the valve port 12, the flow rate of the throttle valve is positively correlated with the pressure difference in the throttle valve, and the portion of the flow rate curve of the throttle valve corresponding to the first column section 221 is an oblique line. Meanwhile, the flow rate at the valve port when the valve needle 20 moves to the first ridge line L1 in the first reference surface S1 is Q1, and the above setting of the second preset distance h2 ensures that the flow rate at the valve port when the valve needle 20 moves to the first ridge line L1 in the first reference surface S1 is greater than the flow rate when the throttle valve is fully closed, so as to ensure that the throttle valve can normally operate.

In the present embodiment, the second predetermined distance h2 is 1.2mm.

It should be noted that the value of the second preset distance h2 is not limited to this, and may be adjusted according to the working condition and the use requirement. Optionally, the second preset distance h2 is 1.1mm, and 1.15mm, and 1.22mm.

Optionally, the first preset distance h1 and the second preset distance h2 satisfy: h2-h1 is more than or equal to 0.75mm and less than or equal to 0.85mm. Thus, the arrangement ensures that the flow rate at the valve port is larger when the valve needle 20 moves to the position where the first ridge L1 is in the first reference surface S1 than when the throttle valve is fully closed, so as to ensure that the throttle valve can normally operate; on the other hand, the phenomenon that the service life of the valve needle is influenced by large impact on the valve needle due to the fact that the flow rate is suddenly increased because the flow rate difference between the two positions is too large is avoided.

In the embodiment, the difference between the first preset distance h1 and the second preset distance h2 is 0.85mm.

It should be noted that, a value of a difference between the first preset distance h1 and the second preset distance h2 is not limited thereto, and may be adjusted according to a working condition and a use requirement. Optionally, the difference between the first preset distance h1 and the second preset distance h2 is 0.78mm, and 0.82mm.

Optionally, when the valve needle 20 moves to the fully opened state, a third preset distance h3 is provided between the reference line and the intersection line of the second reference surface S2 and the conical surface, and the third preset distance h3 is greater than or equal to 2.35mm and less than or equal to 2.45mm. Thus, the above setting of the third preset distance h3 ensures that the flow rate at the valve port when the valve needle 20 moves to the full open state is greater than the flow rate when the valve needle 20 moves until the first ridge L1 is within the first reference plane S1, so as to ensure that the throttle valve can operate normally.

In the present embodiment, the third predetermined distance h3 is 2.4mm.

It should be noted that the value of the third preset distance h3 is not limited to this, and may be adjusted according to the working condition and the use requirement. Optionally, the third preset distance h3 is 2.38mm, and 2.42mm.

As shown in fig. 3 to 5 and 7 to 10, the valve seat 10 further has a medium inlet 13, and the medium inlet 13 communicates with the installation chamber 11 through the valve port 12. Wherein the media inlet 13 is trumpet-shaped, and the size of the media inlet 13 gradually decreases along the direction from the media inlet 13 to the installation cavity 11. Thus, the horn-shaped medium inlet 13 is beneficial to medium flowing in the medium inlet, so that the medium flowing into the medium inlet 13 is smoother, the noise generated in the operation process of the throttle valve is further reduced, and the use experience of a user is improved.

Optionally, the media inlet 13 is flared and the corresponding central angle θ satisfies: theta is more than or equal to 15 degrees and less than or equal to 90 degrees. Like this, under the prerequisite of guaranteeing disk seat 10's structural strength, above-mentioned setting makes the central angle theta value of medium entry 13 more nimble to satisfy different user demand and operating mode, also promoted staff's processing flexibility.

Optionally, the media inlet 13 is flared and the corresponding central angle θ satisfies: theta is more than or equal to 49 degrees and less than or equal to 51 degrees.

Optionally, the maximum inner diameter Φ D of the trumpet-shaped medium inlet 13 satisfies: d is more than or equal to 6mm and less than or equal to 7mm.

Optionally, the adjustment segment 22 further comprises a conical segment 223. The conical section 223 is connected to an end of the second section 222 away from the first section 221, a second ridge L2 is formed at the connection of the second section 222 and the conical section 223, and the flow curve further includes a second inflection point C 'between the first inflection point B' and the end point. When the valve needle 20 moves until the second ridge line L2 is in the first reference surface S1, a fourth preset distance h4 is formed between the reference line and an intersection line of the second reference surface S2 and the conical surface, and the fourth preset distance h4 is greater than or equal to 1.35mm and less than or equal to 1.45mm; the first preset distance h1 is more than or equal to 0.3mm and less than or equal to 0.4mm; the second preset distance h2 and the fourth preset distance h4 satisfy the following condition: h4-h2 is less than or equal to 0.2mm; or, the flow rate of the valve port 12 at the second turning point C' is Q3, and Q1/Q3 is greater than or equal to 0.3 and less than or equal to 0.5, and the fourth preset distance h4 and the second preset distance h2 satisfy: h4-h2 is less than or equal to 0.5mm. Thus, the above setting of the fourth preset distance h4 ensures that the flow rate at the valve port when the valve needle 20 moves to the second ridge L2 in the first reference surface S1 is greater than the flow rate when the valve needle 20 moves to the first ridge L1 in the first reference surface S1, so as to ensure that the throttle valve can operate normally.

In this embodiment, the flow rate of the valve port 12 at the second turning point C' is Q3, and satisfies that Q1/Q3 is greater than or equal to 0.3 and less than or equal to 0.5, and the fourth predetermined distance h4 and the second predetermined distance h2 satisfy: h4-h2 is less than or equal to 0.5mm. The fourth predetermined distance h4 is 1.4mm. It should be noted that the value of the fourth preset distance h4 is not limited to this, and may be adjusted according to the working condition and the use requirement. Optionally, the fourth preset distance h4 is 1.38mm or 1.42mm.

As shown in fig. 1 to 3, the throttle valve further includes a screen assembly 30, a plug 40 and a spring 50. Wherein a screen assembly 30 is provided at the medium inlet 13 for filtering impurities in the medium, and a spring is sleeved on the needle 20 for applying an elastic force to the needle 20 moving toward the medium inlet 13. The spring 50 has opposite ends abutting the needle 20 and the plug 40, respectively.

In the present embodiment, the distance between the intersection line of the second reference surface S2 and the conical surface and the reference line is defined as the valve needle opening h of the throttle valve, and for different diameters of the valve port 12, the corresponding relationship between the flow Q and the opening h of the throttle valve at different positions on the flow curve is shown in table 1:

TABLE 1 corresponding relationship table between flow and opening of throttle valve at different positions on flow curve

Among them, a flow rate curve of the throttle valve in the first embodiment is shown in fig. 11, a flow rate curve of the throttle valve in the second embodiment is shown in fig. 12, a flow rate curve of the throttle valve in the third embodiment is shown in fig. 13, a flow rate curve of the throttle valve in the fourth embodiment is shown in fig. 14, and a flow rate curve of the throttle valve in the fifth embodiment is shown in fig. 15. The starting point A 'in the flow curve is the corresponding opening h1 and flow rate when the valve needle is in the closed state, the end point D' is the corresponding opening h3 and flow rate when the valve needle is in the fully open state, the first turning point B 'is the corresponding opening h2 and flow rate when the valve needle section B is located at the valve port, and the second turning point C' is the corresponding opening h4 and flow rate when the valve needle section C is located at the valve port.

Specifically, the valve needle opening is h1 (as shown in fig. 7) when the differential pressure across the valve is 0MPa, and the corresponding flow rate is 0. When the pressure difference between the front and the rear of the valve is larger than 0MPa, the valve needle is driven by pressure along with the gradual increase of the pressure, so that the opening degree of the valve needle is increased, and the flow is increased due to the increase of the opening degree of the valve needle. The defect that the existing throttle valve is always closed and has no flow when the pressure difference between the front and the back of the valve is 0-0.30MPa is overcome. When the pressure difference before and after the valve is more than 0MPa, the valve can be divided into an intermediate working condition, a rated working condition and a medium-temperature rated working condition. In the middle working condition, the section A-B of the valve needle is positioned in the valve port (as shown in figure 8), and the opening degree of the valve needle is between 1.0mm and 1.3 mm. Under the rated working condition, the C-D section of the valve needle is positioned in the valve port (as shown in figure 10), and the opening degree of the valve needle is between 1.9 and 2.2 mm. And under part of the working conditions, such as the medium-temperature rated working condition and the low-wind-speed rated working condition, the section B-C of the valve needle is positioned in the valve port (as shown in figure 9). The flow area of the section A-B and the section C-D is fixed, the flow changes with the valve pressure difference, the section B-C is a conical surface variable flow area section, and the flow is influenced with the pressure difference and the flow area, so that the flow curve of the throttle valve is in a multi-section broken line type.

The application also provides a refrigeration system (not shown) comprising the throttle valve as described above, the rated refrigeration capacity C of the refrigeration system being greater than or equal to 2.5KW and less than or equal to 7.5KW.

Optionally, the refrigerant of the refrigeration system is HFC32 or HFC410A.

Alternatively, when the refrigerant of the refrigeration system is HFC32 and the rated refrigerating capacity of the refrigeration system is 2.5 to 2.7KW, the throttle valve of d =1.0mm in the first embodiment is employed.

Alternatively, when the refrigerant of the refrigeration apparatus is HFC32 and the rated refrigerating capacity is 3 to 3.8KW, the throttle valve of d =1.2mm in the second embodiment is employed.

Alternatively, when the refrigerant of the refrigeration apparatus is HFC32 and the rated refrigerating capacity is 5 to 5.4KW, the throttle valve of d =1.3mm in the third embodiment is employed.

Alternatively, when the refrigerant of the refrigeration apparatus is HFC32 and the rated refrigerating capacity is 7.2 to 7.5KW, the throttle valve of d =1.5mm in the fourth embodiment is employed.

Alternatively, when the refrigerant of the refrigeration apparatus is HFC410A and the rated refrigerating capacity is 2.5 to 2.7KW, the throttle valve of d =1.2mm in the second embodiment is employed.

Alternatively, when the refrigerant of the refrigeration apparatus is HFC410A and the rated refrigerating capacity is 3 to 3.8KW, the throttle valve of d =1.3mm in the third embodiment is used.

Alternatively, when the refrigerant of the refrigeration apparatus is HFC410A and the rated refrigerating capacity is 5 to 5.4KW, the throttle valve of d =1.5mm in the fourth embodiment is used.

Alternatively, when the refrigerant of the refrigeration apparatus is HFC410A and the rated refrigerating capacity is 7.2 to 7.5KW, the throttle valve of d =1.7mm in the fifth embodiment is employed.

Example two

The throttle valve in the second embodiment is different from the first embodiment in that: the adjustment segment 22 does not include the conical segment 223.

In the present embodiment, the end of the second column section 222 away from the first column section 221 is an arc-shaped surface, and the flow curve further includes an arc-shaped line section between the first turning point B' and the end point. Wherein the second preset distance h2 is greater than or equal to 1.75mm and less than or equal to 1.85mm. Thus, in the process that the end of the second column section 222 moves in the valve port 12, the flow area is gradually reduced, the flow rate of the throttling valve is related to the pressure difference and the flow area in the throttling valve, the arrangement of the arc section can avoid the noise generated by the larger impact between the end of the second column section 222 and the medium, and the use experience of a user is further improved.

As shown in fig. 16 to 23, the distance between the intersection line of the second reference surface S2 and the conical surface and the reference line is defined as the opening h of the throttle valve, and the corresponding relationship between the flow Q and the opening h of the throttle valve at different positions on the flow curve for different diameters of the valve port 12 is shown in table 2:

TABLE 2 corresponding relationship table between flow and opening of throttle valve at different positions on flow curve

Among them, a flow rate curve of the throttle valve in the first embodiment is shown in fig. 19, a flow rate curve of the throttle valve in the second embodiment is shown in fig. 20, a flow rate curve of the throttle valve in the third embodiment is shown in fig. 21, a flow rate curve of the throttle valve in the fourth embodiment is shown in fig. 22, and a flow rate curve of the throttle valve in the fifth embodiment is shown in fig. 23. The starting point A ' in the flow curve is the corresponding valve needle opening h1 and flow when the valve needle is in the closed state, the terminal point C ' is the corresponding valve needle opening h3 and flow when the valve needle is in the fully open state, and the first turning point B ' is the corresponding valve needle opening h2 and flow when the valve needle section B is positioned at the valve port.

Specifically, when the differential pressure across the valve is 0MPa, the valve needle opening is h1 (as shown in fig. 16), and the corresponding flow rate is 0. When the pressure difference between the front and the back of the valve is larger than 0MPa, the pressure drives the valve needle along with the gradual increase of the pressure, so that the opening degree of the valve needle is increased, and the flow is increased due to the increase of the opening degree of the valve needle. The defect that the existing throttle valve is always closed and has no flow when the pressure difference between the front and the back of the valve is 0-0.30MPa is overcome. When the pressure difference before and after the valve is more than 0MPa, the pressure difference before and after the valve can be divided into rated working condition and overload working condition when the pressure difference before and after the valve is more than 0 MPa. When in rated working condition, the section A-B of the valve needle is positioned in the valve port (as shown in figure 17), and the opening degree of the valve needle is between 1.4 and 1.6 mm; in the overload condition, the section B-C of the valve needle is positioned in the valve port (as shown in figure 18), and the opening degree of the valve needle is larger than 1.9mm. The section A-B is a conical variable flow area section, and the flow is influenced by the pressure difference and the flow area, so that the flow curve of the throttle valve is in a multi-section broken line shape.

EXAMPLE III

The difference between the throttle valve in the third embodiment and the first embodiment is that: the structure of the adjustment segment 22 is different.

As shown in fig. 24 to 32, the outer peripheral surface of the second column section 222 is a tapered surface, and the adjustment section 22 further includes a third column section 224. The third column 224 is connected to an end of the conical section 223 far from the second column 222, and a third ridge L3 is formed at the connection between the third column 224 and the conical section 223. The flow curve further includes a third inflection point located between the second inflection point and the end point, and the third ridge L3 corresponds to the third inflection point. When the valve needle 20 moves to the third ridge line L3 in the first reference surface S1, a fifth preset distance h5 is provided between the reference line and the intersection line of the second reference surface S2 and the conical surface, the fifth preset distance h5 is greater than or equal to 1.75mm and less than or equal to 1.85mm, and the fifth preset distance h5 and the fourth preset distance h4 satisfy the following relationship: h5-h4 is more than or equal to 0.4mm and less than or equal to 0.5mm; the flow rate of the valve port 12 at the third turning point is Q4, and Q1/Q4 is more than or equal to 0.4 and less than or equal to 0.7. Thus, the above setting of the fifth preset distance h5 ensures that the flow rate at the valve port when the valve needle 20 moves to the third ridge L3 in the first reference surface S1 is greater than the flow rate when the valve needle 20 moves to the first ridge L1 in the first reference surface S1, so as to ensure that the throttle valve can operate normally.

In the present embodiment, the distance between the intersection line of the second reference surface S2 and the conical surface and the reference line is defined as the opening h of the throttle valve, and the corresponding relationship between the flow Q and the opening h of the throttle valve at different positions on the flow curve for different diameters of the valve port 12 is shown in table 3:

TABLE 3 corresponding relationship table between flow and opening of throttle valve at different positions on flow curve

Among them, a flow rate curve of the throttle valve in the first embodiment is shown in fig. 28, a flow rate curve of the throttle valve in the second embodiment is shown in fig. 29, a flow rate curve of the throttle valve in the third embodiment is shown in fig. 30, a flow rate curve of the throttle valve in the fourth embodiment is shown in fig. 31, and a flow rate curve of the throttle valve in the fifth embodiment is shown in fig. 32. The starting point a ' in the flow curve is the valve needle opening h1 and flow rate corresponding to the valve needle in the closed state, the end point E ' is the valve needle opening h3 flow rate corresponding to the valve needle in the fully open state, the first turning point B ' is the flow rate of the valve needle opening h2 corresponding to the valve port where the valve needle cross section B is located, the second turning point C ' is the flow rate of the valve needle opening h4 corresponding to the valve port where the valve needle cross section C is located, and the third turning point D ' is the flow rate of the valve needle opening h5 corresponding to the valve port where the valve needle cross section D is located.

Specifically, when the differential pressure across the valve is 0MPa, the valve needle opening is h1 (as shown in fig. 24), and the corresponding flow rate is 0. When the pressure difference between the front and the back of the valve is larger than 0MPa, the pressure drives the valve needle along with the gradual increase of the pressure, so that the opening degree of the valve needle is increased, and the flow is increased due to the increase of the opening degree of the valve needle. The defect that the existing throttle valve is always closed and has no flow when the pressure difference between the front and the back of the valve is 0-0.30MPa is overcome. When the pressure difference between the front and the rear of the valve is more than 0MPa, the valve can be divided into an intermediate working condition, a rated working condition and an overload working condition. Wherein, the A-B section of the valve needle is positioned in the valve port (as shown in figure 25) under the middle working condition, and the opening degree of the valve needle is between 0.9 mm and 1.1 mm. Under a rated working condition, the C-D section of the valve needle is positioned in the valve port (as shown in figure 26), and the opening degree of the valve needle is between 1.5mm and 1.7 mm. During an overload condition, section D-E of the valve needle (as shown in FIG. 27) is located within the valve port. The flow areas of the section A-B and the section C-D are fixed, the flow changes along with the valve pressure difference, the section D-E is a conical surface variable flow area section, and the flow is influenced along with the pressure difference and the flow area, so that the flow curve of the throttle valve is in a multi-section broken line type.

From the above description, it can be seen that the above-mentioned embodiments of the present invention achieve the following technical effects:

when the throttle valve is in a closed state, a first preset distance h1 is reserved between the intersecting line of the second reference surface S2 and the conical surface and the reference line, so that a gap is reserved between the valve port and at least part of the adjusting section, and the design is similar to the flow design when the throttle valve is completely closed. Therefore, when the refrigeration system is started, part of the medium can enter the installation cavity through the gap before the medium pushes the valve needle to move, and the phenomenon that the friction between the medium and the throttle valve is increased due to the fact that the pressure in the front of and behind the valve port is increased rapidly is avoided until the medium can push the valve needle to move and throttle the medium.

Compared with the design of no flow when the throttle valve is fully closed in the prior art, the throttle valve has the flow design when the throttle valve is fully closed, on one hand, the pressure at the valve port is reduced, on the other hand, the rapid increase of the pressure in the front and the back of the valve port is avoided, the friction force between a medium and the throttle valve is reduced, the problem that the throttle valve is prone to generating noise when a refrigeration system is started in the prior art is solved, the noise when the refrigeration system is started is reduced, and the use experience of a user is improved.

It is obvious that the above described embodiments are only some of the embodiments of the present invention, and not all of them. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts shall belong to the protection scope of the present invention.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular forms "a", "an", and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise.

It should be noted that the terms "first," "second," and the like in the description and claims of this application and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used is interchangeable under appropriate circumstances such that the embodiments of the application described herein are capable of operation in sequences other than those illustrated or described herein.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (10)

1. A throttle valve, comprising:

a valve seat (10) having a mounting cavity (11) and a valve port (12) communicated with the mounting cavity (11), wherein at least part of the cavity wall of the mounting cavity (11) forms a first reference surface S1, and the valve port (12) is arranged on the first reference surface S1;

a valve needle (20) movably disposed within the valve seat (10); the valve needle (20) comprises a body section (21) and an adjusting section (22) connected with the body section (21), the body section (21) is arranged in the installation cavity (11) in a penetrating manner, the adjusting section (22) is arranged in the valve port (12) in a penetrating manner, and the adjusting section (22) reciprocates under the pushing of a medium entering the valve port (12) so as to adjust the opening degree of the valve port (12); the outer peripheral surface of one end, connected with the adjusting section (22), of the body section (21) is a conical surface, and the size of the conical surface is gradually increased along the direction from the adjusting section (22) to the body section (21);

wherein the valve port (12) forms a reference line on the first reference surface S1, and a second reference surface S2 perpendicular to the first reference surface S1 is formed by passing through the reference line; when the throttle valve is in a closed state, a first preset distance h1 is reserved between the intersection line of the second reference surface S2 and the conical surface and the reference line, a gap is reserved between the valve port (12) and at least part of the adjusting section (22), and the first preset distance h1 is greater than or equal to 0.3mm and smaller than or equal to 0.4mm.

2. A choke valve according to claim 1, characterized in that the shape of the adjusting segment (22), the internal pressure difference of the choke valve and the diameter of the valve port (12) are arranged such that the flow curve of the choke valve has the following characteristics:

the flow curve comprises a starting point A ', a first turning point B ' and an end point, the starting point A ' corresponds to the closing state of the throttle valve, the flow of the valve port (12) at the starting point A ' is Q0, the flow of the valve port (12) at the first turning point B ' is Q1, the end point corresponds to the full-opening state of the throttle valve, the flow of the valve port (12) at the end point is Q2, and the conditions that Q0 is greater than 0 and Q1 is greater than Q2 are met.

3. The throttling valve according to claim 2, characterized in that the adjustment section (22) comprises:

a first column section (221);

a second section (222), wherein the body section (21) is connected with the second section (222) through the first section (221), and a first ridge line L1 is formed at the joint of the first section (221) and the second section (222); when the valve needle (20) moves until the first ridge line L1 is in the first reference surface S1, a second preset distance h2 is reserved between the reference line and an intersection line of the second reference surface S2 and the conical surface, and the second preset distance h2 is larger than or equal to 1.05mm and smaller than or equal to 1.85mm.

4. A throttle valve according to claim 3, characterized in that the end of the second column section (222) remote from the first column section (221) is an arc-shaped surface, the flow curve further comprising an arc segment between the first turning point B' and the end point; wherein the second preset distance h2 is greater than or equal to 1.75mm and less than or equal to 1.85mm.

5. The throttle valve according to claim 3, characterized in that a third predetermined distance h3 is provided between the reference line and an intersection line of the second reference surface S2 and the tapered surface when the valve needle (20) moves to the full open state, and the third predetermined distance h3 is 2.35mm or more and 2.45mm or less.

6. The throttling valve according to claim 3, characterized in that the adjusting section (22) further comprises:

a conical section (223) connected to an end of the second section (222) remote from the first section (221), the connection of the second section (222) and the conical section (223) forming a second ridge L2, the flow curve further comprising a second inflection point C 'between the first inflection point B' and the end point;

when the valve needle (20) moves until the second ridge line L2 is in the first reference surface S1, a fourth preset distance h4 is reserved between the reference line and the intersection line of the second reference surface S2 and the conical surface, and the fourth preset distance h4 is greater than or equal to 1.35mm and smaller than or equal to 1.45mm; the first preset distance h1 is more than or equal to 0.3mm and less than or equal to 0.4mm; the second preset distance h2 and the fourth preset distance h4 satisfy the following condition: h4-h2 is less than or equal to 0.2mm; or, the flow rate of the valve port (12) at the second turning point C' is Q3, and Q1/Q3 is greater than or equal to 0.3 and less than or equal to 0.5, and the fourth preset distance h4 and the second preset distance h2 satisfy: h4-h2 is less than or equal to 0.5mm.

7. The choke valve according to claim 6, characterized in that the outer circumference of the second section (222) is a conical surface, the adjustment section (22) further comprising:

a third cylindrical section (224) connected to an end of the conical section (223) away from the second cylindrical section (222), wherein a third ridge L3 is formed at a connection between the third cylindrical section (224) and the conical section (223), and the flow rate curve further includes a third turning point located between the second turning point C' and the end point;

when the valve needle (20) moves to the third edge line L3 in the first reference surface S1, a fifth preset distance h5 is provided between the reference line and the intersection line of the second reference surface S2 and the conical surface, the fifth preset distance h5 is greater than or equal to 1.75mm and less than or equal to 1.85mm, and the fifth preset distance h5 and the fourth preset distance h4 satisfy the following condition: h5-h4 is more than or equal to 0.4mm and less than or equal to 0.5mm; the flow of the valve port (12) at the third turning point is Q4, and the condition that Q1/Q4 is more than or equal to 0.4 and less than or equal to 0.7 is met.

8. A choke valve according to claim 1, characterized in that the valve seat (10) also has a medium inlet (13), which medium inlet (13) communicates with the mounting chamber (11) through the valve port (12); wherein the media inlet (13) is trumpet-shaped, and the size of the media inlet (13) is gradually reduced along the direction from the media inlet (13) to the installation cavity (11).

9. Throttling valve according to claim 8, characterized in that the medium inlet (13) is trumpet-shaped and the corresponding central angle θ satisfies: theta is more than or equal to 15 degrees and less than or equal to 90 degrees.

10. Refrigeration system, characterized in that it comprises a throttle valve according to any one of claims 1 to 9, the refrigeration system having a nominal refrigeration capacity C of greater than or equal to 2.5KW and less than or equal to 7.5KW.

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