CN116086054A - Bidirectional throttle valve, first air conditioning system and second air conditioning system - Google Patents

Bidirectional throttle valve, first air conditioning system and second air conditioning system Download PDF

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Publication number
CN116086054A
CN116086054A CN202111307151.8A CN202111307151A CN116086054A CN 116086054 A CN116086054 A CN 116086054A CN 202111307151 A CN202111307151 A CN 202111307151A CN 116086054 A CN116086054 A CN 116086054A
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CN
China
Prior art keywords
valve
port
way
throttle
air conditioning
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202111307151.8A
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Chinese (zh)
Inventor
林元阳
宣利华
冯晶
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhejiang DunAn Hetian Metal Co Ltd
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Zhejiang DunAn Hetian Metal Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Zhejiang DunAn Hetian Metal Co Ltd filed Critical Zhejiang DunAn Hetian Metal Co Ltd
Priority to CN202111307151.8A priority Critical patent/CN116086054A/en
Priority to PCT/CN2022/125871 priority patent/WO2023078081A1/en
Publication of CN116086054A publication Critical patent/CN116086054A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/20—Excess-flow valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Multiple-Way Valves (AREA)

Abstract

The invention relates to the technical field of valves, in particular to a bidirectional throttle valve and an air conditioning system with the same. The bidirectional throttle valve comprises a valve pipe, wherein a first valve core and the inner wall of a first valve port are matched to form a first circulation channel; a second circulation channel is formed between the second valve core and the inner wall of the second valve port in a matching way; when the first valve port and the second valve port are opened, the flow area of the first flow channel is larger than that of the second flow channel, and the second valve core is matched with the second valve port to realize throttling. The invention also provides an air conditioning system which comprises the bidirectional throttle valve. Compared with the prior art, the invention has the advantages that: when the first valve port and the second valve port are opened, the flow area of the first flow channel is larger than that of the second flow channel, so that the flow quantity is increased, the bidirectional flow unidirectional throttling function of the bidirectional throttling valve can be realized, and the requirement of low pressure and large flow under the defrosting working condition can be met.

Description

Bidirectional throttle valve, first air conditioning system and second air conditioning system
Technical Field
The invention relates to the technical field of valves, in particular to a bidirectional throttle valve, a first air conditioning system and a second air conditioning system.
Background
The throttle valve is mainly applied to an air conditioner refrigerating system and is an important component of the refrigerating system. The two-way throttle valve is mainly applied to a cold-warm type air conditioning system, and adopts two throttle valve components to be arranged in parallel or in series so as to realize the two-way circulation function.
The functions of the existing one-way throttle valve and the two-way throttle valve are limited, the one-way throttle valve can only realize one-way circulation, and the two-way throttle valve has smaller flow when realizing two-way circulation, and cannot meet the requirements of two-way circulation and one-way throttle of part of machine types and the requirement of low-pressure large flow on one defrosting side under defrosting working conditions.
Disclosure of Invention
In view of the foregoing, in an embodiment of the present invention, a bidirectional throttle valve is provided.
In order to solve the technical problems, the invention provides the following technical scheme:
the two-way throttle valve comprises a valve pipe, wherein a first valve core assembly and a second valve core assembly are respectively arranged at two ends in the valve pipe, the first valve core assembly comprises a first valve core, a first valve port is arranged in the first valve core assembly, the first valve core is movably arranged in the valve pipe and can open/close the first valve port, and a first circulation channel is formed by matching the first valve core with the inner wall of the first valve port; the second valve core assembly comprises a second valve core, a second valve port is arranged in the second valve core assembly, the second valve core is movably arranged in the valve pipe and can open/close the second valve port, and a second circulation channel is formed between the second valve core and the inner wall of the second valve port in a matching way; when the first valve port and the second valve port are opened, the flow area of the first flow channel is larger than that of the second flow channel, and the second valve core is matched with the second valve port to realize throttling.
It can be appreciated that when the first valve port and the second valve port are opened, the flow area of the first flow channel is larger than that of the second flow channel, so that the flow is increased, the bidirectional flow and the unidirectional throttling function of the bidirectional throttle valve can be realized, and the requirement of low pressure and high flow under the defrosting working condition can be met when the bidirectional throttle valve is positioned under the defrosting working condition.
In one embodiment, the valve pipe is connected to an air conditioning system pipeline, a communication piece is further arranged in the valve pipe, and the first valve core component is installed at one end of the communication piece; the communication piece is provided with a first channel, and the first channel is communicated with the first valve port; the caliber of the first valve port is D 1 The diameter of the first channel is D 2 The diameter of the air conditioning system pipeline is D 3 ，D 1 、D 2 And D 3 The following relationship is satisfied: d (D) 2 ≥D 1 ≥D 3 。
It will be appreciated that by having the caliber D at the first valve port 1 Diameter D of the first channel 2 And diameter D of the air conditioning system pipeline 3 The relation is satisfied: d (D) 2 ≥D 1 ≥D 3 Therefore, when the first valve port is opened, the first valve core component does not generate throttling, and full circulation is realized.
In one embodiment, the valve pipe is connected to an air conditioning system pipeline, a communication piece is further arranged in the valve pipe, and the first valve core component is installed at one end of the communication piece; the caliber of the first valve port is D 1 The diameter of the air conditioning system pipeline is D 3 ，D 1 And D 3 The following relationship is satisfied: d (D) 1 ＜D 3 。
It will be appreciated that by having the caliber D at the first valve port 1 And diameter D of the air conditioning system pipeline 3 The relation is satisfied: d (D) 1 ＜D 3 Therefore, when the first valve port is opened, the first valve core component is partially throttled, and small hole throttling is realized.
In one embodimentWherein the caliber of the second valve port is D 4 ，D 1 And D 4 The following relationship is satisfied: d (D) 4 ＞D 1 ＞(1/3)D 4 。
It will be appreciated that by having the caliber D at the first valve port 1 And the caliber of the second valve port is D 4 The relation is satisfied: d (D) 4 ＞D 1 ＞(1/3)D 4 So that when the first valve port is opened, the orifice restriction is further realized at the first valve port.
In one embodiment, the first valve core assembly comprises a first valve seat, the first valve core is movably arranged in the first valve seat, and the first valve port is arranged on the first valve seat; a gap flow area S between the side wall of the first valve core and the inner wall of the first valve seat 1 Is larger than the flow area S at the first valve port 2 。
It will be appreciated that by providing a clearance flow area S between the first valve spool and the first valve seat 1 Is larger than the flow area S at the first valve port 2 The method comprises the steps of carrying out a first treatment on the surface of the So that no throttling is created at the first valve port, thereby increasing the flow rate at the first valve port.
In one embodiment, the second valve core assembly comprises a second valve seat, the second valve core is movably arranged in the second valve seat, and the second valve port is arranged on the second valve seat; the clearance flow area between the side wall of the second valve core and the inner wall of the second valve seat is smaller than the flow area at the second valve port.
It will be appreciated that by having the gap flow area between the second valve spool and the second valve seat be smaller than the flow area at the second valve port, a restriction is created at the second valve port.
In one embodiment, the second valve core assembly comprises a second valve seat, and the second valve core is movably arranged in the second valve seat; the second valve seat is internally provided with a second sealing head and an elastic piece, the second sealing head is arranged at one end of the second valve seat, which is far away from the first valve core assembly, and two ends of the elastic piece are respectively abutted to the second valve core and the second sealing head, so that the second valve core has a trend of reducing the flow area of the second flow channel.
It can be appreciated that by arranging the elastic member in the second valve seat, the second valve core moves under fluid pressure while overcoming the elastic force of the elastic member, so as to realize the throttling at the second valve port.
In one embodiment, the first passage is provided as a linear passage inclined with respect to the axial direction of the communication member.
It can be appreciated that by arranging the first channel and the second channel to be linear channels inclined relative to the axial direction of the communicating member, the flow resistance is smaller when the fluid flows in the first channel and the second channel, and the stability of the bidirectional throttle valve is better.
The invention also provides the following technical scheme in one embodiment:
a first air conditioning system, the first air conditioning system includes compressor, first heat exchanger, second heat exchanger, four-way valve and at least 2 two-way throttle valve, two-way throttle valve includes first two-way throttle valve and second two-way throttle valve, first heat exchanger connect in the cross valve between the C mouth and the first two-way throttle valve be close to its one end of second case subassembly, the second heat exchanger connect in the cross valve between the E mouth and the second two-way throttle valve be close to its one end of second case subassembly, first two-way throttle valve be close to its one end of first case subassembly with the second two-way throttle valve be close to its one end of first case subassembly is connected, the compressor connect in between the D mouth of four-way valve and the S mouth of four-way valve.
It will be appreciated that by having the first heat exchanger connected between the C port of the four-way valve and the end of the first bi-directional throttle valve adjacent to its second spool assembly, the second heat exchanger is connected between the E port of the four-way valve and the end of the second bi-directional throttle valve adjacent to its second spool assembly, the end of the first bi-directional throttle valve adjacent to its first spool assembly is connected with the end of the second bi-directional throttle valve adjacent to its first spool assembly, and the compressor is connected between the D port of the four-way valve and the S port of the four-way valve, the problem of large loss of cold along the way when the system piping is long is solved.
In one embodiment, the number of the second heat exchangers is at least two, the number of the second bidirectional throttle valves is at least two, each second heat exchanger is connected between an E port of the four-way valve and one end of each second bidirectional throttle valve close to the second valve core assembly, and one end of each second bidirectional throttle valve close to the first valve core assembly is mutually connected.
It will be appreciated that by having each of the second heat exchangers connected between the E port of the four-way valve and the end of each of the second two-way throttles adjacent to its second spool assembly, the ends of each of the second two-way throttles adjacent to its first spool assembly are interconnected, thereby enabling a plurality of the second two-way throttles to be connected in parallel in the air conditioning system for use in a one-to-many application in the air conditioning system.
The invention also provides the following technical scheme in one embodiment:
the second air conditioning system comprises a compressor, a first heat exchanger, a second heat exchanger, a four-way valve and at least 1 bidirectional throttle valve, wherein the first heat exchanger is connected between an E port of the four-way valve and one end, close to a first valve core component, of the bidirectional throttle valve, the second heat exchanger is connected between a C port of the four-way valve and one end, close to a second valve core component, of the bidirectional throttle valve, and the compressor is connected between a D port of the four-way valve and an S port of the four-way valve.
It can be appreciated that, through making first heat exchanger connect in between the E mouth of cross valve and the one end that two-way choke valve is close to its first case subassembly, the second heat exchanger connect in between the C mouth of cross valve and the one end that two-way choke valve is close to its second case subassembly, the compressor connect in between the D mouth of cross valve and the S mouth of cross valve to the refrigerant flow need promote by a wide margin when solving the air conditioner defrosting under the long-term refrigeration condition.
Compared with the prior art, when the first valve port and the second valve port are opened, the bidirectional throttle valve provided by the embodiment of the invention can increase the flow quantity by enabling the flow area of the first flow channel to be larger than the flow area of the second flow channel, thereby realizing the bidirectional flow unidirectional throttle function of the bidirectional throttle valve and meeting the requirement of low pressure and large flow under the defrosting working condition when the bidirectional throttle valve is in the defrosting working condition.
Drawings
FIG. 1 is a schematic diagram of a two-way throttle valve according to the present invention;
FIG. 2 is a schematic diagram of a bidirectional flow direction of a bidirectional throttle valve provided by the present invention;
FIG. 3 is a schematic view of the structure of the inside of a two-way throttle valve tube provided by the invention;
FIG. 4 is a schematic structural view of a communication member according to the present invention;
FIG. 5 is a schematic view of a first valve seat according to the present invention;
FIG. 6 is a schematic diagram of a second valve seat according to the present invention;
FIG. 7 is a schematic cross-sectional view of the structure at A-A in FIG. 1;
FIG. 8 is a schematic cross-sectional view of the structure at B-B in FIG. 1;
FIG. 9 is a schematic diagram of a first air conditioning system according to the present invention;
FIG. 10 is a partially enlarged schematic illustration of the portion X in FIG. 9;
FIG. 11 is an enlarged partial schematic view at Y in FIG. 9;
fig. 12 is a schematic diagram of a second air conditioning system according to the present invention.
The symbols in the drawings are as follows:
100. a two-way throttle valve; 10. a valve tube; 11. a first valve chamber; 12. a second valve chamber; 20. a first valve core assembly; 21. a first valve seat; 211. a first valve port; 212. a first seat cavity; 22. a first valve core; 23. a first end socket; 30. a second spool assembly; 31. a second valve seat; 311. a second valve port; 312. a second seat cavity; 32. a second valve core; 33. a second end socket; 34. an elastic member; 40. a communication member; 41. a first channel; 42. a second channel; 43. a first chamber; 44. a second chamber; 200. an air conditioning system; 201. a first air conditioning system; 202. a second air conditioning system; 50. a compressor; 60. a first heat exchanger; 61. a second heat exchanger; 70. a four-way valve; 80. a first two-way throttle valve; 81. a second two-way throttle valve; 90. an air conditioning system pipeline.
Detailed Description
The present invention will be further described in detail with reference to the drawings and the detailed description, in order to make the objects, technical solutions and advantages of the present invention more apparent. It should be understood that the detailed description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the invention.
It is noted that when an element is referred to as being "mounted to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "secured to" another element, it can be directly secured to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "left," "right," and the like are used herein for illustrative purposes only and are not meant to be the only embodiment.
Unless defined otherwise, 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 invention belongs. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "or/and" as used herein includes any and all combinations of one or more of the associated listed items.
Referring to fig. 1 to 12, in an embodiment of the present invention, a bi-directional throttle valve 100 is provided, the bi-directional throttle valve 100 is applied to an air conditioning system 200, and the bi-directional throttle valve 100 is mainly applied to the air conditioning system 200, and two throttle valve assemblies are connected in parallel or in series to realize a bi-directional circulation function.
The functions of the existing one-way throttle valve and the two-way throttle valve are limited, the one-way throttle valve can only realize one-way circulation, and the two-way throttle valve has smaller flow when realizing two-way circulation, and cannot meet the requirements of two-way circulation and one-way throttle of part of machine types and the requirement of low-pressure large flow on one defrosting side under defrosting working conditions.
In order to solve the problems of the existing bidirectional throttle valve, in an embodiment of the present invention, a bidirectional throttle valve 100 is provided, which includes a valve tube 10, two ends in the valve tube 10 are respectively provided with a first valve core assembly 20 and a second valve core assembly 30, the first valve core assembly 20 includes a first valve core 22, the first valve core assembly 20 has a first valve port 211 therein, the first valve core 22 is movably disposed in the valve tube 10 and can open/close the first valve port 211, and a first flow channel is formed by cooperation between the first valve core 22 and an inner wall of the first valve port 211; the second valve core assembly 30 comprises a second valve core 32, a second valve port 311 is arranged in the second valve core assembly 30, the second valve core 32 is movably arranged in the valve pipe 10 and can open/close the second valve port 311, and a second circulation channel is formed by matching the second valve core 32 with the inner wall of the second valve port 311; when the first valve port 211 and the second valve port 311 are opened, the flow area of the first flow channel is larger than that of the second flow channel, and the second valve core 32 is matched with the second valve port 311 to realize throttling.
When the first valve port 211 and the second valve port 311 are opened, the flow area of the first flow channel is larger than the flow area of the second flow channel, so that the flow rate is increased, the bidirectional flow unidirectional throttling function of the bidirectional throttle valve 100 is realized, and the requirement of low pressure and high flow rate under the defrosting working condition can be met when the bidirectional throttle valve 100 is in the defrosting working condition.
As shown in fig. 1, a communication member 40 is further provided in the valve tube 10. The communication member 40 is provided in the valve tube 10 and divides the interior of the valve tube 10 into a first valve chamber 11 and a second valve chamber 12. The communication member 40 is provided with a first chamber 43, a second chamber 44, a first passage 41 and a second passage 42, the first chamber 43 is located at an end of the communication member 40 close to the first valve chamber 11, the second chamber 44 is located at an end of the communication member 40 close to the second valve chamber 12, the first passage 41 communicates with the first chamber 43 and the second valve chamber 12, and the second passage 42 communicates with the second chamber 44 and the first valve chamber 11. The first valve core assembly 20 is mounted in the first chamber 43 for automatically adjusting the flow rate between the first passage 41 and the first valve chamber 11. The second spool assembly 30 is mounted at the second chamber 44 for regulating the flow between the second passage 42 and the second valve chamber 12.
As shown in fig. 2, when the two-way throttle valve 100 is in operation, fluid may enter the second passage 42 from the first valve chamber 11, then the second chamber 44, then the second spool assembly 30, and finally the second valve chamber 12. Fluid may also enter the first passage 41 from the second valve chamber 12, then enter the first chamber 43, then enter the first valve spool assembly 20, and finally enter the first valve chamber 11. In this way, the bidirectional throttle valve 100 can realize bidirectional flow through the valve pipe 10, the communication member 40, the first valve core assembly 20 and the second valve core assembly 30, and has fewer parts and very simple structure. During installation, the assembly work of the bidirectional throttle valve 100 can be completed only by installing the communicating piece 40 in the valve pipe 10 and installing the first valve core assembly 20 and the second valve core assembly 30 at two ends of the communicating piece 40 respectively, the installation process is very simple, the probability of occurrence of defects in the assembly process is reduced, and the improvement of the product consistency is facilitated, so that the production cost of the bidirectional throttle valve 100 is greatly reduced. "product uniformity" refers to the fact that, during mass production, the different products remain substantially the same.
As shown in fig. 3 and 4, the first passage 41 is provided as a linear passage inclined with respect to the axial direction of the communication member 40. In this way, the flow resistance is smaller when the fluid flows in the first passage 41, so that the stability of the two-way throttle valve 100 is better. Accordingly, the second passage 42 is also provided as a linear passage inclined with respect to the axial direction of the communication member 40. Likewise, the flow resistance is smaller when the fluid flows in the second passage 42, so that the stability of the two-way throttle valve 100 is better.
In the present embodiment, the communication member 40, the first spool assembly 20, and the second spool assembly 30 are coaxially disposed. The coaxial arrangement makes the overall occupied space of the communication member 40, the first valve core assembly 20 and the second valve core assembly 30 smaller, thereby facilitating the miniaturization design of the valve tube 10 and greatly reducing the occupied space of the two-way throttle valve 100.
As shown in fig. 5, the first valve spool assembly 20 includes a first valve seat 21. The first valve seat 21 has a first seat cavity 212 therein, the first valve core 22 is movably disposed in the first seat cavity 212, and the first valve port 211 is opened on the first valve seat 21. The end cover of the first valve seat 21, which is far away from the second valve core assembly 30, is provided with a first sealing head 23, and a gap which is communicated with the first seat cavity 212 and the first valve cavity 11 is reserved between the first sealing head 23 and the first valve seat 21 so as to allow fluid to pass through. When the flow area of the first valve port 211 decreases to zero, the first valve port 211 is closed. When the fluid pressure in the first channel 41 is greater than the self gravity of the first valve core 22, the fluid pushes the first valve core 22 to move so as to open the first valve port 211 or increase the flow area of the first valve port 211, and the fluid sequentially flows through the first valve port 211 and the first seat cavity 212 from the first channel 41 and finally enters the first valve cavity 11. When the fluid pressure in the first passage 41 is smaller than the self gravity of the first valve spool 22, the first valve spool 22 moves reversely and reduces the flow area of the first valve port 211, even closing the first valve port 211.
As shown in fig. 6, the second spool assembly 30 includes a second valve seat 31. The second valve seat 31 has a second seat cavity 312 therein, the second valve core 32 is movably disposed in the second seat cavity 312, and the second valve port 311 is disposed on the second valve seat 31. The end cover of the second valve seat 31 far away from the first valve core assembly 20 is provided with a second sealing head 33, and a gap for communicating the second seat cavity 312 and the second valve cavity 12 is reserved between the second sealing head 33 and the second valve seat 31 so as to allow fluid to pass through.
Further, an elastic member 34 is further disposed in the second valve seat 31, and two ends of the elastic member 34 are respectively abutted against the second valve core 32 and the second sealing head 33, so that the second valve core 32 has a tendency of reducing the flow area of the second flow channel. When the flow area of the second valve port 311 is zero, the second valve port 311 is in a closed state, and when the flow area of the second valve port 311 is greater than zero, the second valve port 311 is in an open state. Adjusting the size of the flow area of the second valve port 311 includes both adjusting the size of the flow area in the open state of the second valve port 311 and switching the second valve port 311 between the open state and the closed state. When the flow area of the second valve port 311 decreases to zero, the second valve port 311 is closed. When the fluid pressure in the second passage 42 is greater than the elastic force of the elastic member 34, the fluid pushes the second valve element 32 to move so as to compress the elastic member 34 and open the second valve port 311 or increase the flow area of the second valve port 311, and the greater the fluid pressure in the second passage 42, the greater the flow area of the second valve port 311, so that the fluid sequentially flows from the second passage 42 through the second valve port 311 and the second seat cavity 312, and finally enters the second valve chamber 12. When the fluid pressure in the second passage 42 is smaller than the elastic force of the elastic member 34, the second valve element 32 moves reversely and reduces the flow area of the second valve port 311 even closes the third valve port under the elastic restoring force of the elastic member 34.
Because the existing bidirectional throttle valve is generally in a bidirectional flow and bidirectional throttle structure, the flow of fluid is generally small, and for the defrosting operation in the air conditioning system 200, a sufficient amount of fluid is generally required to defrost the condensed water in the air conditioning system 200, if the bidirectional throttle valve 100 is in bidirectional throttle, the requirement of large flow in the defrosting operation cannot be satisfied at all.
In the two-way throttle 100, one of the valve core assemblies is in a full flow or small orifice throttle configuration, and the other valve core assembly is in a throttle configuration. The flow rate of the full flow or small hole throttle structure is larger than that of the throttle structure. This achieves that both throttling and high flow conditions under defrost conditions can be met in the two-way throttle 100.
In this embodiment, the first spool assembly 20 is provided in a full flow or orifice throttling configuration. Of course, in other embodiments, the second valve element assembly 30 may be configured in a full flow or orifice throttling configuration, without limitation.
When the first valve core assembly 20 is fully circulated, the caliber of the first valve port 211 is D 1 The first channel 41 has a diameter D 2 The air conditioning system piping 90 has a diameter D 3 ，D 1 、D 2 And D 3 The relation is satisfied: d (D) 2 ≥D 1 ≥D 3 . In designing the diameters of the first port 211 and the first passage 41, D will be 1 、D 2 And D 3 The relation is satisfied: d (D) 2 ≥D 1 ≥D 3 When the first valve port 211 is opened, the first valve core assembly 20 does not generate throttling, so that full circulation is realized.
When the fluid flows into the second valve chamber 12 from the air conditioning system pipe 90, the fluid flows into the first passage 41 from the gap between the second valve seat 31 and the valve pipe 10, and the flow passage area becomes large at this time because the diameter of the first passage 41 is larger than the diameter of the air conditioning system pipe 90, thereby realizing full flow.
When the first valve core assembly 20 realizes orifice throttling, the caliber of the first valve port 211 is D 1 The air conditioning system piping 90 has a diameter D 3 ，D 1 And D 3 The following relationship is satisfied: d (D) 1 ＜D 3 . When the caliber of the first valve port 211 is designed, D is as follows 1 And D 3 The relation is satisfied: d (D) 1 ＜D 3 So that when the first valve port 211 is opened, the first valve core assembly 20 is partially throttled, and orifice throttling is realized.
When fluid flows into the second valve chamber 12 from the air conditioning system pipe 90, fluid flows into the first valve port 211 from the gap between the second valve seat 31 and the valve pipe 10, and the diameter of the first valve port 211 is smaller than that of the air conditioning system pipe 90, so that the flow passage area is reduced, and orifice throttling is realized.
Further, in order to better realize orifice throttling of the first valve core assembly 20, the caliber of the second valve port 311 is D 4 ，D 1 And D 4 The relation is satisfied: d (D) 4 ＞D 1 ＞(1/3)D 4 . When the calibers of the first valve port 211 and the second valve port 311 are designed, D will be 1 And D 4 The relation is satisfied: d (D) 4 ＞D 1 ＞(1/3)D 4 So that when the first valve port 211 is opened, the orifice restriction is further realized at the first valve port 211.
It is noted that, when the fluid flows into the first valve chamber 11 from the air conditioning system pipe 90, the fluid flows into the second valve port 311 from the gap between the first valve seat 21 and the valve pipe 10, and the flow passage area is reduced at this time because the diameter of the second valve port 311 is smaller than that of the air conditioning system pipe 90, thereby realizing the throttling. Why is the flow rate of the second valve element assembly 30 still less than the flow rate of the first valve element assembly 20 when the orifice restriction is designed? The following differences in structure between the first spool assembly 20 and the second spool assembly 30 are mainly attributed.
As shown in fig. 7 to 8, the difference in flow area is first. A gap flow area S between the side wall of the first spool 22 and the inner wall of the first valve seat 21 1 Greater than the flow area S at the first port 211 2 . The gap flow area between the side wall of the second valve element 32 and the inner wall of the second valve seat 31 is smaller than the flow area at the second valve port 311. Based on this, the process of pushing the first valve element 22 open by the fluid is significantly easier than the process of pushing the second valve element 32 open by the fluid due to the pressure difference, and the opening passage area of the first valve port 211 is larger than that of the second valve port 311, so the flow rate of the first valve element assembly 20 is larger than that of the second valve element assembly 30.
And secondly with respect to the difference in elastic structure. That is, only the first valve core 22 capable of moving in the first seat cavity 212 is provided in the first seat cavity 212, that is, when the fluid pushes the first valve core 22 away from the first valve port 211, only the gravity of the first valve core 22 needs to be overcome, and since the first valve core 22 is not connected with other components, after the fluid pushes the first valve core 22 away, the impact force of the fluid is gradually smaller than the gravity of the first valve core 22, otherwise the first valve core 22 does not move towards the direction of the first valve port 211, and at this time, large-flow circulation is realized at the first valve port 211; in addition to the second valve core 32, the second seat cavity 312 is further provided with an elastic member 34 with two ends respectively connected with the second sealing head 33 and the second valve core 32, that is, when the fluid pushes the second valve core 32 away from the second valve port 311, the elastic force of the elastic member 34 needs to be overcome in addition to the self gravity of the second valve core 32, and after the fluid pushes the second valve core 32 away, the second valve core 32 moves towards the second valve port 311 due to the elastic restoring force of the elastic member 34, and the flow at the second valve port 311 is gradually reduced due to the trend.
In summary, because of the difference in flow area and the elastic structure between the first spool assembly 20 and the second spool assembly 30, the flow rate at the first valve port 211 is greater than the flow rate at the second valve port 311 despite the design of the first valve port 211 as a small orifice throttling structure.
Preferably, the elastic member 34 is a spring; of course, in other embodiments, the elastic member 34 may also have other elastic structures, which are not limited herein.
As shown in fig. 9 to 11, the present invention also provides a first air conditioning system 201, the first air conditioning system 201 includes a compressor 50, a first heat exchanger 60, a second heat exchanger 61, a four-way valve 70, and a two-way throttle valve 100, the two-way throttle valve 100 includes a first two-way throttle valve 80 and a second two-way throttle valve 81, the first heat exchanger 60 is connected between a C port of the four-way valve 70 and an end of the first two-way throttle valve 80 adjacent to the second spool assembly 30 of the first two-way throttle valve 80, the second heat exchanger 61 is connected between an E port of the four-way valve 70 and an end of the second two-way throttle valve 81 adjacent to the second spool assembly 30 of the second two-way throttle valve 81, an end of the first two-way throttle valve 80 adjacent to the first spool assembly 20 of the second two-way throttle valve 81 is connected with an end of the second two-way throttle valve 81 adjacent to the first spool assembly 20 of the second two-way throttle valve 81, and the compressor 50 is connected between a D port of the four-way valve 70 and an S port of the four-way valve 70.
The first air conditioning system 201 is mainly a system with more components and longer air conditioning system pipelines 90, and the applicable bidirectional throttle valve 100 is a bidirectional throttle valve 100 with one end throttled and the other end fully circulated. When the first air conditioning system 201 is refrigerating, the low-temperature and low-pressure gas is compressed by the compressor 50 to form high-temperature and high-pressure gas, the high-temperature and high-pressure gas enters the first heat exchanger 60 through the four-way valve 70, and is condensed into medium-temperature and high-pressure liquid through the first heat exchanger 60, the medium-temperature and high-pressure liquid enters the second valve cavity 12 of the first bidirectional throttle valve 80, flows into the first channel 41 through the gap between the second valve seat 31 and the valve tube 10, then enters the first valve port 211, the medium-temperature and high-pressure liquid pushes up the first valve core 22 into the second seat cavity and then enters the first valve cavity 11, and because the fluid is fully circulated at the first valve port 211, the medium-temperature and high-pressure liquid flows through the first bidirectional throttle valve 80 only equivalently to flow through the first air conditioning system pipeline 90, and is not throttled, the medium-temperature and high-pressure liquid flows into the first valve cavity 11 of the second bidirectional throttle valve 81 after flowing out of the first valve cavity 11 of the first bidirectional throttle valve 80, flows into the second channel 42 through the gap between the first valve seat 21 and the valve tube 10, then flows into the second valve cavity 42, at the second valve port 311, the medium-temperature and high-pressure liquid flows into the second valve cavity 12 through the second valve cavity 311, and finally flows into the second valve cavity 61 through the second valve cavity 12 through the second valve port 311, and finally flows into the low-temperature valve cavity through the second valve cavity, and then flows into the second valve cavity through the second valve cavity, and is compressed by the low-pressure valve cavity, and finally enters the second valve cavity, and enters the second valve cavity, and is cooled valve cavity, and is cooled, and finally enters the high-temperature valve cavity, and is cooled.
When the first air conditioning system 201 heats, the low-temperature and low-pressure gas is compressed by the compressor 50 to form high-temperature and high-pressure gas, the high-temperature and high-pressure gas enters the second heat exchanger 61 through the four-way valve 70, and is released by the second heat exchanger 61 to form medium-temperature and high-pressure liquid, the medium-temperature and high-pressure liquid enters the second valve cavity 12 of the second bidirectional throttle valve 81, flows into the first channel 41 through a gap between the second valve seat 31 and the valve tube 10 and then enters the first valve port 211, the medium-temperature and high-pressure liquid pushes the first valve core 22 open and enters the first seat cavity 212 and then enters the first valve cavity 11, and the medium-temperature and high-pressure liquid flows through the second bidirectional throttle valve 81 only to be equivalent to flowing through the first air conditioning system pipeline 90 at the first valve port 211, and is not throttled, the medium-temperature and high-pressure gas flows into the first valve cavity 11 of the first bidirectional throttle valve 80 after flowing out of the first valve cavity 11 of the second bidirectional throttle valve 81, flows into the second channel 42 through a gap between the first valve seat 21 and the valve tube 10, then flows into the first valve cavity 42, the medium-temperature and high-pressure liquid flows into the second valve cavity 311 through the second valve cavity 60 through the second valve port 211, and finally flows into the second valve cavity 60 through the second valve cavity 60, and then flows into the medium-chamber 60 through the second valve cavity 60, and is cooled by the medium-temperature and flows into the medium-temperature and high-pressure valve cavity 60, and finally, and flows into the medium-pressure medium through the second valve cavity 60, and is cooled through the medium valve cavity, and is cooled.
It is noted that the second heat exchanger 61 and the second two-way throttle valve 81 may be connected in series in a plurality of pipes, the specific number being dependent on the specific situation of the air conditioning system 200. That is, the first air conditioning system 201 includes at least 2 second heat exchangers 61 and at least 2 second double-direction throttle valves 81, each second heat exchanger 61 is connected between the E port of the four-way valve 70 and one end of each second double-direction throttle valve 81 adjacent to the second spool assembly 30 of the second double-direction throttle valve 81, and one end of each second double-direction throttle valve 81 adjacent to the first spool assembly 20 of the second double-direction throttle valve 81 is connected to each other.
The bidirectional throttle valve 100 with the full circulation of the first valve core assembly 20 and the throttle of the second valve core assembly 30 is applied to the first air conditioning system 201, is mainly applied to one-to-many occasions, and solves the problem that when the air conditioning system pipeline 90 is longer, the refrigeration and heating cycle shares one bidirectional throttle valve 100, and the refrigeration loss is larger along the way.
As shown in fig. 12, the present invention further provides a second air conditioning system 202, where the second air conditioning system 202 includes a compressor 50, a first heat exchanger 60, a second heat exchanger 61, a four-way valve 70, and 1 two-way throttle valve 100, the first heat exchanger 60 is connected between an E port of the four-way valve 70 and an end of the two-way throttle valve 100 near the first valve core assembly 20 of the second two-way throttle valve 100, the second heat exchanger 61 is connected between a C port of the four-way valve 70 and an end of the two-way throttle valve 100 near the second valve core assembly 30 of the second two-way throttle valve 100, and the compressor 50 is connected between a D port of the four-way valve 70 and an S port of the four-way valve 70.
The second air conditioning system 202 is mainly a system with few components and short air conditioning system pipeline 90, and the applicable bidirectional throttle valve 100 is a bidirectional throttle valve 100 with one end throttled and the other end in small hole circulation. When the second air conditioning system 202 is refrigerating, the low-temperature and low-pressure gas is compressed by the compressor 50 to form high-temperature and high-pressure gas, the high-temperature and high-pressure gas enters the first heat exchanger 60 through the four-way valve 70, is condensed into medium-temperature and high-pressure liquid through the first heat exchanger 60, the medium-temperature and high-pressure liquid enters the first valve cavity 11 of the two-way throttle valve 100, flows into the second channel 42 through a gap between the first valve seat 21 and the valve pipe 10, then enters the second valve port 311, the medium-temperature and high-pressure liquid pushes the second valve core 32 open, enters the second valve cavity 312 and then enters the second valve cavity 12, and because the fluid is throttled at the second valve port 311, the medium-temperature and high-pressure liquid flows through the two-way throttle valve 100 to be throttled into low-temperature and low-pressure liquid or low-temperature and low-pressure gas-liquid two-phase state, flows out of the second valve cavity 12 of the two-way throttle valve 100, flows into the second heat exchanger 61 again, is evaporated through the second heat exchanger 61 to form low-temperature and low-pressure vapor, and finally enters the compressor 50 through the valve 70, so that the circulation is completed.
When the second air conditioning system 202 is defrosted, the low-temperature and low-pressure gas is compressed by the compressor 50 to form high-temperature and high-pressure gas, the high-temperature and high-pressure gas enters the second heat exchanger 61 through the four-way valve 70, and is condensed into medium-temperature and high-pressure liquid through the second heat exchanger 61, the medium-temperature and high-pressure liquid enters the second valve cavity 12 of the bidirectional throttle valve 100, flows into the first channel 41 through a gap between the second valve seat 31 and the valve pipe 10, then enters the first valve port 211, at this time, the medium-temperature and high-pressure liquid pushes the first valve core 22 open, enters the first valve cavity 212 and then enters the first valve cavity 11, and because the fluid is throttled into a low-temperature and low-pressure liquid or gas-liquid two-phase medium at the first valve port 211, the flow area is increased, the medium of which is low-temperature and low-pressure liquid or gas-liquid two-phase flows into the first heat exchanger 60 after flowing out of the first valve cavity 11 of the bidirectional throttle valve 100, the medium is evaporated through the first heat exchanger 60 to form low-temperature and low-pressure gas, and finally enters the compressor 50 through the four-way valve 70, thereby completing defrosting circulation.
The bidirectional throttle valve 100 with the small hole throttle of the first valve core assembly 20 and the throttle of the second valve core assembly 30 is applied to the second air conditioning system 202, is mainly applied to the occasions of refrigeration and freezing, and solves the problem that the refrigerant flow needs to be greatly improved when the air conditioning system 200 is defrosted in a long-term refrigeration environment.
It should be noted that the air conditioning system 200 is either the first air conditioning system 201 or the second air conditioning system 202.
According to the bidirectional throttle valve 100 provided by the invention, when the first valve port 211 and the second valve port 311 are opened, the flow area of the first flow channel is larger than that of the second flow channel, so that the bidirectional flow unidirectional throttle function of the bidirectional throttle valve 100 can be realized, and the requirement of low pressure and large flow under the defrosting working condition can be met when the bidirectional throttle valve 100 is in the defrosting working condition.
The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.
The above examples illustrate only a few embodiments of the invention, which are described in detail and are not to be construed as limiting the scope of the invention. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the invention, which are all within the scope of the invention. Accordingly, the scope of protection of the present invention is to be determined by the appended claims.

Claims (11)

1. The two-way throttle valve comprises a valve pipe (10), wherein a first valve core assembly (20) and a second valve core assembly (30) are respectively arranged at two ends in the valve pipe (10), the first valve core assembly (20) comprises a first valve core (22), a first valve port (211) is arranged in the first valve core assembly (20), the first valve core (22) is movably arranged in the valve pipe (10) and can open/close the first valve port (211), and a first circulation channel is formed by matching between the first valve core (22) and the inner wall of the first valve port (211);
the second valve core assembly (30) comprises a second valve core (32), a second valve port (311) is arranged in the second valve core assembly (30), the second valve core (32) is movably arranged in the valve pipe (10) and can open/close the second valve port (311), and a second circulation channel is formed between the second valve core (32) and the inner wall of the second valve port (311) in a matching way;
the valve is characterized in that when the first valve port (211) and the second valve port (311) are opened, the flow area of the first flow channel is larger than that of the second flow channel, and the second valve core (32) is matched with the second valve port (311) to realize throttling.
2. The two-way throttle valve according to claim 1, wherein the valve tube (10) is connected to an air conditioning system pipeline (90), a communication member (40) is further provided in the valve tube (10), and the first valve core assembly (20) is mounted at one end of the communication member (40);
the communication piece (40) is provided with a first channel (41), and the first channel (41) is communicated with the first valve port (211);
the caliber of the first valve port (211) is D 1 The diameter of the first channel (41) is D 2 The diameter of the air conditioning system pipeline (90) is D 3 ，D 1 、D 2 And D 3 The following relationship is satisfied:
D 2 ≥D 1 ≥D 3 。
3. the two-way throttle valve according to claim 1, wherein the valve tube (10) is connected to an air conditioning system pipeline (90), a communication member (40) is further provided in the valve tube (10), and the first valve core assembly (20) is mounted at one end of the communication member (40);
the caliber of the first valve port (211) is D 1 The diameter of the air conditioning system pipeline (90) is D 3 ，D 1 And D 3 The following relationship is satisfied:
D 1 ＜D 3 。
4. a two-way throttle valve as claimed in claim 3, characterized in thatCharacterized in that the caliber of the second valve port (311) is D 4 ，D 1 And D 4 The following relationship is satisfied:
D 4 ＞D 1 ＞(1/3)D 4 。
5. the two-way throttle valve according to claim 1, wherein the first valve core assembly (20) comprises a first valve seat (21), the first valve core (22) is movably arranged in the first valve seat (21), and the first valve port (211) is opened in the first valve seat (21);
a flow area S of a gap between a side wall of the first valve element (22) and an inner wall of the first valve seat (21) 1 Is larger than the flow area S at the first valve port (211) 2 。
6. The two-way throttle valve according to claim 1, wherein the second valve core assembly (30) comprises a second valve seat (31), the second valve core (32) is movably arranged in the second valve seat (31), and the second valve port (311) is opened in the second valve seat (31);
a flow area of a gap between a side wall of the second valve element (32) and an inner wall of the second valve seat (31) is smaller than a flow area at the second valve port (311).
7. The two-way throttle valve of claim 1, wherein the second spool assembly (30) includes a second valve seat (31), the second spool (32) being movably disposed within the second valve seat (31);
be equipped with second head (33) and elastic component (34) in second disk seat (31), second head (33) are located second disk seat (31) are kept away from first case subassembly (20) one end, the both ends of elastic component (34) butt respectively in second case (32) with second head (33), so that second case (32) have the trend of reduction the area of circulation of second circulation passageway.
8. A two-way throttle valve according to claim 2, characterized in that the first passage (41) is provided as a straight passage inclined with respect to the axial direction of the communication member (40).
9. A first air conditioning system comprising a compressor (50), a first heat exchanger (60), a second heat exchanger (61), a four-way valve (70) and at least 2 bi-directional throttles as claimed in any one of claims 1, 2, 5-7, said bi-directional throttles comprising a first bi-directional throttle (80) and a second bi-directional throttle (81), said first heat exchanger (60) being connected between a C port of said four-way valve (70) and an end of said first bi-directional throttle (80) adjacent to said second spool assembly (30), said second heat exchanger (61) being connected between an E port of said four-way valve (70) and an end of said second bi-directional throttle (81) adjacent to said second spool assembly (30), an end of said first bi-directional throttle (80) adjacent to said first spool assembly (20) being connected between a C port of said four-way valve (70) and an end of said second bi-directional throttle (81) adjacent to said first spool assembly (20), said second heat exchanger (61) being connected between a D port of said four-way valve (70) and said four-way valve (70).
10. The first air conditioning system according to claim 9, characterized in that there are at least two second heat exchangers (61) and at least two second double-direction throttle valves (81), each second heat exchanger (61) being connected between an E-port of the four-way valve (70) and an end of each second double-direction throttle valve (81) adjacent to its second spool assembly (30), each second double-direction throttle valve (81) being connected to each other adjacent to an end of its first spool assembly (20).
11. A second air conditioning system, characterized in that the second air conditioning system comprises a compressor (50), a first heat exchanger (60), a second heat exchanger (61), a four-way valve (70) and at least 1 bidirectional throttle valve according to any one of claims 1, 3-7, wherein the first heat exchanger (60) is connected between an E port of the four-way valve (70) and an end of the bidirectional throttle valve close to the first valve core assembly (20), the second heat exchanger (61) is connected between a C port of the four-way valve (70) and an end of the bidirectional throttle valve close to the second valve core assembly (30), and the compressor (50) is connected between a D port of the four-way valve (70) and an S port of the four-way valve (70).
CN202111307151.8A 2021-11-05 2021-11-05 Bidirectional throttle valve, first air conditioning system and second air conditioning system Pending CN116086054A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN202111307151.8A CN116086054A (en) 2021-11-05 2021-11-05 Bidirectional throttle valve, first air conditioning system and second air conditioning system
PCT/CN2022/125871 WO2023078081A1 (en) 2021-11-05 2022-10-18 Bidirectional throttle valve, first air conditioning system and second air conditioning system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202111307151.8A CN116086054A (en) 2021-11-05 2021-11-05 Bidirectional throttle valve, first air conditioning system and second air conditioning system

Publications (1)

Publication Number Publication Date
CN116086054A true CN116086054A (en) 2023-05-09

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ID=86201166

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202111307151.8A Pending CN116086054A (en) 2021-11-05 2021-11-05 Bidirectional throttle valve, first air conditioning system and second air conditioning system

Country Status (1)

Country Link
CN (1) CN116086054A (en)

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