WO2026026906A1 - 切换阀 - Google Patents

切换阀

Info

Publication number
WO2026026906A1
WO2026026906A1 PCT/CN2025/111781 CN2025111781W WO2026026906A1 WO 2026026906 A1 WO2026026906 A1 WO 2026026906A1 CN 2025111781 W CN2025111781 W CN 2025111781W WO 2026026906 A1 WO2026026906 A1 WO 2026026906A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
valve
valve port
piston assembly
channel
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
PCT/CN2025/111781
Other languages
English (en)
French (fr)
Inventor
杨忠宇
蔡培裕
方启迪
王傅钢
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 Artificial Environment Co Ltd
Original Assignee
Zhejiang Dunan Artificial Environment 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.)
Filing date
Publication date
Priority claimed from CN202411047213.XA external-priority patent/CN121497857A/zh
Priority claimed from CN202421841966.3U external-priority patent/CN222950475U/zh
Priority claimed from CN202421834340.XU external-priority patent/CN222963391U/zh
Priority claimed from CN202422838717.5U external-priority patent/CN223725511U/zh
Application filed by Zhejiang Dunan Artificial Environment Co Ltd filed Critical Zhejiang Dunan Artificial Environment Co Ltd
Publication of WO2026026906A1 publication Critical patent/WO2026026906A1/zh
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/08—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks
    • F16K11/085—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with cylindrical plug
    • 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

Definitions

  • This disclosure relates to the field of fluid control technology, and more specifically, to a switching valve.
  • switching valves can move within the valve cavity of the valve body under the drive of fluid pressure. If the pressure of the fluid acting on the switching valve is too low, the switching valve's operating capability will be low, and sometimes the valve may even fail to close or open completely, affecting the valve's reliability.
  • This disclosure provides a switching valve, including a valve body, a piston assembly, and an elastic element.
  • the valve body includes an inner cavity with a valve port.
  • the piston assembly is movably disposed within the inner cavity for blocking or opening the valve port.
  • the elastic element is used to keep the piston assembly in a balanced state.
  • the balanced state means that, under no fluid impact, the piston assembly remains stationary relative to the valve body.
  • a throttling channel communicating with the valve port is formed between the piston assembly and the cavity wall.
  • Figure 1 shows an exploded view of the switching valve according to the first embodiment of this disclosure.
  • Figure 2 shows a top view of the switching valve according to the first embodiment of this disclosure.
  • Figure 3 shows a cross-sectional view along section line A-A in Figure 2.
  • Figure 4 shows the flow area curve of the switching valve when the ratio of the maximum flow area of the throttling channel to the maximum flow area of the valve port is >3/10, and the piston assembly is in a balanced state.
  • Figure 5 shows the flow area curve of the switching valve when the ratio of the maximum flow area of the throttling channel to the maximum flow area of the valve port is ⁇ 3/10 when the piston assembly is in a balanced state.
  • Figure 6 shows the flow resistance curve of the switching valve when the ratio of the maximum flow area of the throttling channel to the maximum flow area of the valve port is >3/10, and the piston assembly is in a balanced state.
  • Figure 7 shows the flow resistance curve of the switching valve when the ratio of the maximum flow area of the throttling channel to the maximum flow area of the valve port is ⁇ 3/10 when the piston assembly is in equilibrium.
  • Figure 8 shows a cross-sectional view of the switching valve according to the second embodiment of this disclosure.
  • Figure 9 shows a cross-sectional view of the switching valve according to the third embodiment of this disclosure.
  • Figure 10 shows a cross-sectional view of a switching valve according to a fourth embodiment of this disclosure.
  • Figure 11 shows a cross-sectional view of a switching valve according to a fifth embodiment of this disclosure.
  • Figure 12 shows a perspective view of the piston assembly of the switching valve according to the fifth embodiment of this disclosure.
  • Figure 13 shows an exploded view of the switching valve according to the sixth embodiment of this disclosure.
  • Figure 14 shows a cross-sectional view of a switching valve according to a sixth embodiment of this disclosure.
  • Figure 15 shows a schematic diagram of the elastic resultant force exerted on the piston assembly by a pair of first elastic elements when the free length of the first elastic element in the switching valve of the sixth embodiment of this disclosure is in three different ranges.
  • Figure 16 shows a schematic diagram of the resultant elastic force curve when a pair of first elastic elements and a pair of second elastic elements act simultaneously on the piston assembly.
  • Figure 17 shows an exploded view of the switching valve according to the seventh embodiment of this disclosure.
  • Figure 18 shows a cross-sectional view of a switching valve according to a seventh embodiment of the present disclosure.
  • Figure 19 shows an exploded view of an exemplary embodiment of the switching valve of the eighth embodiment of this disclosure.
  • Figure 20 shows a longitudinal cross-sectional view along the plug rod of an exemplary embodiment of the switching valve of the eighth embodiment of the present disclosure.
  • Figure 21 shows a longitudinal cross-sectional view along the plug rod of another exemplary embodiment of the switching valve of the eighth embodiment of the present disclosure.
  • Figure 22 shows a schematic diagram of a piston assembly in an exemplary embodiment of the switching valve of the eighth embodiment of the present disclosure
  • Figure 23 shows a schematic diagram of the valve body in an exemplary embodiment of the switching valve of the eighth embodiment of the present disclosure.
  • the switching valve of this embodiment includes a valve body 100, a piston assembly 200, and an elastic element.
  • the valve body 100 includes an inner cavity 101 with valve ports (102a, 102b); the piston assembly 200 is movably disposed within the inner cavity 101 for blocking or opening the valve ports; the elastic element is used to keep the piston assembly 200 in a balanced state; wherein, when the piston assembly 200 is in a balanced state, a throttling channel communicating with the valve ports is formed between the piston assembly 200 and the cavity wall of the inner cavity 101.
  • the ratio of the maximum flow area of the throttling channel to the maximum flow area of the valve ports is ⁇ 3/10, which allows the fluid to continuously generate a large driving force on the piston assembly from the balanced state to the complete closure of the valve ports, thus improving the switching valve's operating capability.
  • the valve ports include a first valve port 102a and a second valve port 102b, which are spaced apart along the movement direction of the piston assembly 200.
  • the piston assembly 200 is used to seal the first valve port 102a and the second valve port 102b respectively.
  • the maximum flow area of the first valve port 102a is S11
  • the maximum flow area of the second valve port 102b is S12.
  • the maximum flow area of a valve orifice refers to the cross-sectional area of fluid flow when the valve orifice is fully open, i.e., the opening area of the valve orifice.
  • the flow area of a throttling channel refers to the opening area of the flow channel.
  • the elastic element includes a pair of first elastic elements 310, which are defined as a first elastic portion 310a and a second elastic portion 310b, respectively.
  • the first elastic portion 310a and the second elastic portion 310b are used to maintain the stability of the piston assembly in a balanced state.
  • the first elastic portion 310a is used to provide a first elastic force to the piston assembly 200 to move toward the position of blocking the second valve port 102b
  • the second elastic portion 310b is used to provide a second elastic force to the piston assembly 200 to move toward the position of blocking the first valve port 102a.
  • the resultant force of the elastic force of the first elastic part 310a and the second elastic part 310b acting on the piston assembly 200 and the gravity of the piston assembly 200 is zero.
  • the valve body 100 may include a valve seat 120 and a valve cover 130.
  • the valve seat 120 has an inner cavity 101, and the valve cover 130 is connected to the valve seat 120.
  • This disclosure does not limit the connection method between the valve cover 130 and the valve seat 120, such as threaded connection, welding, interference fit, etc.
  • the valve cover 130 and the valve seat 120 may be integrally formed.
  • Valve cover 130 has a first opening 131, which communicates with the inner cavity 101.
  • Valve seat 120 has a second opening 121, which also communicates with the inner cavity 101.
  • the first opening 131 can serve as the fluid inlet of the switching valve, communicating with the compressor outlet.
  • the second opening 121 can serve as the fluid outlet of the switching valve, communicating with the compressor inlet.
  • the end of valve seat 120 furthest from valve cover 130 can serve as another fluid inlet of the switching valve, communicating with the compressor outlet. Therefore, the switching valve can be a three-way valve, including two fluid inlets and one fluid outlet.
  • the piston assembly 200 includes a piston rod 210, a first piston 220, and a second piston 230.
  • the first piston 220 is connected to one end of the piston rod 210 and is used to block the first valve port 102a.
  • the second piston 230 is connected to the other end of the piston rod 210 and is used to block the second valve port 102b.
  • the first elastic part 310a and the second elastic part 310b are compression springs and are sleeved on the outer periphery of the plug rod 210.
  • the valve seat 120 includes two first valve sleeves 122 and a second valve sleeve 123 connected between the two first valve sleeves 122.
  • the first valve sleeves 122 and the second valve sleeve 123 are coaxially arranged.
  • the two ends of the second valve sleeve 123 form a first valve port 102a and a second valve port 102b, respectively.
  • valve seat 120 may also have a second valve sleeve 123 instead of the first valve sleeve 122.
  • the inner cavity 101 is provided with a partition 110, which separates the first valve port 102a and the second valve port 102b.
  • the first elastic part 310a is located between the first piston 220 and the partition 110, with one end of the first elastic part 310a abutting against the partition 110 and the other end abutting against the first piston 220.
  • the second elastic part 310b is located between the second piston 230 and the partition 110, with one end of the second elastic part 310b abutting against the partition 110 and the other end abutting against the second piston 230.
  • the partition 110 includes a partition ring 111 and a guide sleeve 112.
  • the partition ring 111 is fixedly connected to the inner circumferential surface of the second valve sleeve 123 and is connected around the outer circumference of the guide sleeve 112.
  • the guide sleeve 112 has a guide hole 110a, and the plug rod 210 is movably inserted into the guide hole 110a of the guide sleeve 112.
  • the stopper 210 is guided and engaged with the guide sleeve 112, which improves the stability of the movement of the stopper 210 and thus improves the reliability of the valve operation.
  • the partition 110 may also include a partition ring 111 that forms a guide hole 110a.
  • the separator ring 111 has a first annular surface 1111 and a second annular surface 1112, which are arranged opposite to each other along the movement direction of the piston assembly 200; the portion of the guide sleeve 112 extending out of the first annular surface 1111 is defined as the first segment 112a, and the first elastic part 310a is sleeved on the outer periphery of the first segment 112a; the portion of the guide sleeve 112 extending out of the second annular surface 1112 is defined as the second segment 112b, and the second elastic part 310b is sleeved on the outer periphery of the second segment 112b.
  • the throttling channel includes a first throttling channel 410 connected to the first valve port 102a and a second throttling channel 420 connected to the second valve port 102b.
  • the maximum flow area of the first throttling channel 410 is S21
  • the maximum flow area of the second throttling channel 420 is S22.
  • a first throttling channel 410 is formed between the outer peripheral surface of the first piston 220 and the inner peripheral surface of one of the first valve sleeves 122
  • a second throttling channel 420 is formed between the outer peripheral surface of the second piston 230 and the inner peripheral surface of the other first valve sleeve 122.
  • the piston assembly 200 moves from a zero flow area at the valve port to a maximum flow area, with a stroke of S1.
  • the stroke is S2.
  • the valve port can be either the first valve port 102a or the second valve port 102b.
  • the horizontal axis in Figures 4 and 5 represents the S2/S1 value of the switching valve, i.e., the opening degree.
  • the vertical axis in Figures 4 and 5 represents the ratio of the valve port flow area to the maximum flow area at different opening degrees. Fluid flows into the valve port through the opening between the piston assembly 200 and the inner wall of the valve seat 120.
  • the valve port flow area is equal to the opening area between the piston assembly 200 and the inner wall of the valve seat 120.
  • the opening area between the piston assembly 200 and the inner wall of the valve seat 120 is the throttling channel area of this embodiment.
  • High-pressure fluid enters the valve port through a throttling channel. After being throttled, the fluid becomes low-pressure fluid and flows out from the second opening 121.
  • the piston assembly 200 is subjected to the pressure difference of the fluid before and after the valve port. Alternatively, the high-pressure fluid directly enters the throttling channel within the valve port and becomes low-pressure fluid, which flows out from the second opening 121.
  • the piston assembly 200 is subjected to the pressure difference of the fluid before and after the valve port. When the flow area of the valve port is zero, the piston assembly 200 is subjected to a pressure difference of F1. When the flow area of the valve port is between zero and the maximum flow area, the piston assembly 200 is subjected to a pressure difference of F2.
  • the horizontal axis in Figures 6 and 7 represents the opening degree of the switching valve.
  • the vertical axis in Figures 6 and 7 represents the F2/F1 values corresponding to different opening degrees of the switching valve.
  • Figures 4 to 7 will all use the first valve port 102a as an example.
  • 0% on the horizontal axis of Figures 4 to 7 represents the position of the piston assembly 200 when the piston assembly 200 blocks the first valve port 102a; 100% on the horizontal axis represents the position of the piston assembly 200 when the first valve port 102a is fully open.
  • the flow area of the valve port is equal to the flow area of the throttling channel, and the ratio of the flow area of the valve port to the maximum flow area of the valve port is approximately 8%, while the value of F2/F1 is approximately 95%. Therefore, it is evident that within the range of 55% opening of the piston assembly 200, the piston assembly 200 is subjected to an increased fluid pressure differential driving force across the valve port, which is beneficial to improving the valve's operating capability.
  • This fluid pressure differential driving force not only overcomes the elastic force applied to the piston assembly 200 by the elastic element but also enables the piston assembly 200 to quickly switch between different operating conditions.
  • the piston assembly 200 when operating to an equilibrium state, can possess a large fluid pressure differential driving force, which ensures the smooth closure of the first valve port 102a.
  • the flow area of the first valve port 102a of the switching valve is relatively small within the opening range of 0% to 55%.
  • the valve opening stroke is between 55% and 100%, the flow area of the first valve port 102a of the switching valve gradually increases.
  • a large fluid pressure differential driving force is generated within the opening range of 0% to 55%.
  • a throttling channel communicating with the valve port is formed between the piston assembly 200 and the cavity wall of the inner cavity 101.
  • the ratio of the maximum flow area of the throttling channel to the maximum flow area of the valve port is ⁇ 3/10.
  • the throttling channel When the piston assembly 200 is in a balanced state, the throttling channel also includes a third throttling channel 430 connected to the first valve port 102a and a fourth throttling channel 440 connected to the second valve port 102b.
  • the maximum flow area of the third throttling channel 430 is S31
  • the maximum flow area of the fourth throttling channel 440 is S32. S31/S11 ⁇ 3/10, S32/S12 ⁇ 3/10.
  • Both the first piston 220 and the second piston 230 have an insertion portion 240.
  • the insertion portion 240 of the first piston 220 extends into the first valve port 102a, and a third throttling channel 430 is formed between the outer peripheral surface of the insertion portion 240 of the first piston 220 and the orifice wall of the first valve port 102a.
  • the insertion portion 240 of the second piston 230 extends into the second valve port 102b, and a fourth throttling channel 440 is formed between the insertion portion 240 of the second piston 230 and the orifice wall of the second valve port 102b.
  • the piston assembly 200 when the piston assembly 200 is in a balanced state, it is provided not only with a first throttling channel 410 and a second throttling channel 420, but also with a third throttling channel 430 and a fourth throttling channel 440, which further improves the operating capability of the switching valve.
  • the switching valve may only have a third throttling channel 430 and a fourth throttling channel 440, without having a first throttling channel 410 and a second throttling channel 420.
  • the flow area of the throttling channel formed between the inner circumferential surface of the first valve sleeve 122 and the piston assembly 200 gradually decreases.
  • the flow area of the first throttling channel 410 gradually decreases
  • the flow area of the second throttling channel 420 gradually decreases.
  • the fluid force generated by throttling gradually increases as the piston assembly 200 gradually blocks the valve ports
  • the elastic force of the first elastic part 310a gradually increases as the piston assembly 200 gradually blocks the valve ports. This overcomes the elastic force that gradually increases as the valve ports close, thereby further improving the valve's actuation capability.
  • the inner circumferential surface of the first valve sleeve 122 has an inner conical surface 1221.
  • the piston assembly 200 can also be prevented from getting stuck in the first valve sleeve 122 due to the throttling channel being too narrow.
  • the piston assembly 200 includes a piston rod 210, a first piston 220, and a second piston 230.
  • the first piston 220 and the second piston 230 are connected to the piston rod 210 and are spaced apart along the axial direction of the piston rod 210.
  • the valve body 100 has a guide portion 132, and the piston rod 210 is guidedly engaged with the guide portion 132.
  • the guide portion 132 can guide the movement of the piston rod 210, thereby preventing the piston rod 210 from deflecting during movement and affecting the sealing performance of the piston sealing the valve port.
  • the guide engagement means that there is a small gap between the piston rod 210 and the guide portion 132.
  • the valve body 100 includes a valve cover 130 and a valve seat 120, the valve seat 120 having an inner cavity 101, and the valve cover 130 connected to the valve seat 120.
  • a guide portion 132 is integrally formed on the valve cover 130.
  • first piston 220 is positioned close to the valve cover 130, and the piston rod 210 has a guide section 211 located on the side of the first piston 220 facing away from the second piston 230.
  • the guide section 211 is guided and engaged with the guide portion 132.
  • the guide portion 132 can be a hole, and the guide segment 211 is guided and engaged with the inner wall surface of the hole.
  • both the first piston 220 and the second piston 230 include a first piston plate 260, a second piston plate 270, and a third piston plate 280.
  • the second piston plate 270 is sandwiched between the first piston plate 260 and the third piston plate 280.
  • the second piston plate 270 may be made of rubber, while the first piston plate 260 and the third piston plate 280 may be made of metal.
  • the first piston plate 260 extends into the valve port.
  • the first piston plate 260 of the first piston 220 extends into the first valve port 102a, and the second piston 230 is located outside the second valve port 102b; when the second piston 230 blocks the second valve port 102b, the first piston plate 260 of the second piston 230 extends into the second valve port 102b, and the first piston 220 is located outside the first valve port 102a.
  • the second piston plate 270 has a second outer conical surface 271 that seals with the valve port. By sealing with the valve port through the second outer conical surface 271, the sealing performance of the piston blocking the valve port can be improved.
  • the outer peripheral surface of the first piston plate 260 has an outer cylindrical surface 261 and two third outer conical surfaces 262, which are symmetrically connected to the two ends of the outer cylindrical surface 261 along the movement direction of the piston assembly 200.
  • the diameter of the outer cylindrical surface 261 is slightly smaller than the diameter of the valve port.
  • the outer peripheral surface of the first piston plate 260 has an outer cylindrical surface 261 and two third outer conical surfaces 262.
  • this can prevent the first piston plate 260 from getting stuck at the edge of the valve port during the valve opening/closing process.
  • the two third outer conical surfaces 262 are symmetrically connected to the two ends of the outer cylindrical surface 261 along the movement direction of the piston assembly 200, there is no need to consider the front or back of the first piston plate 260 when assembling it, thus improving the assembly efficiency.
  • the switching valve of this embodiment includes a valve body 100, a piston assembly 200, and an elastic element.
  • the elastic element may include a pair of first elastic elements 310.
  • the pair of first elastic elements 310 are used to keep the piston assembly 200 in a balanced state.
  • the first elastic element 310 is a compression spring and is sleeved on the outer periphery of the plug rod 210.
  • the inner cavity 101 is provided with a partition 110, which separates the first valve port 102a and the second valve port 102b, and has a guide hole 110a; the plug rod 210 is movably inserted into the guide hole 110a.
  • One of the first elastic members 310 is located between the first piston 220 and the partition 110, with one end of the first elastic member 310 abutting against the partition 110 and the other end abutting against the first piston 220.
  • Another first elastic member 310 is located between the second piston 230 and the partition 110, with one end of the other elastic member 310 abutting against the partition 110 and the other end abutting against the second piston 230.
  • the separator ring 111 has a first annular surface 1111 and a second annular surface 1112, which are arranged opposite to each other along the movement direction of the piston assembly 200; the portion of the guide sleeve 112 extending out of the first annular surface 1111 is defined as the first segment 112a, and one of the first elastic elements 310 is sleeved on the outer periphery of the first segment 112a; the portion of the guide sleeve 112 extending out of the second annular surface 1112 is defined as the second segment 112b, and the other first elastic element 310 is sleeved on the outer periphery of the second segment 112b.
  • the lengths of the pair of first elastic elements 310 are L1 and L2, respectively, where L1 is greater than L2.
  • the free length of the first elastic element 310 is L’, where L2 ⁇ L’ ⁇ (L1 + L2)/2, or L’ ⁇ L1.
  • free length refers to the length of the spring when no external force is applied to either end.
  • Figure 15 shows a schematic diagram of the elastic resultant force exerted by a pair of first elastic elements 310 on the piston assembly 200 when the free length of the first elastic element 310 is in three different intervals.
  • the three different intervals are: L’ ⁇ L1 (curve 1), (L1+L2)/2 ⁇ L’ ⁇ L1 (curve 2), and L2 ⁇ L’ ⁇ (L1+L2)/2 (curve 3).
  • the horizontal axis represents the opening degree of the switching valve
  • the vertical axis represents the ratio of the elastic resultant force corresponding to different opening degrees of the switching valve to the maximum elastic resultant force.
  • the maximum elastic resultant force refers to the elastic resultant force exerted on the piston assembly 200 by a pair of first elastic elements 310 when the piston assembly 200 blocks one of the first valve port 102a and the second valve port 102b.
  • the maximum elastic resultant force exerted on the piston assembly 200 by the three different pairs of first elastic elements 310 corresponding to curves 1, 2, and 3 is equal, that is, curves 1, 2, and 3 have the same starting point and the same ending point.
  • 0% to 50% on the horizontal axis represents the piston assembly 200 moving from the first position (blocking the first valve port 102a) to the equilibrium state, and 50% to 100% represents the piston assembly 200 moving from the equilibrium state to the second position (blocking the second valve port 102b).
  • the force pushing the piston assembly 200 to open the first valve port 102a is mainly the sum of the elastic forces of a pair of first elastic elements 310.
  • the sum of the elastic forces of the pair of first elastic elements 310 opens the first valve port 102a. The greater the sum of the elastic forces of the first elastic elements 310, the more instantly the first valve port 102a can be opened.
  • the key factor for port 102a is that, within the range of 0% to 50% on the horizontal axis, the first valve port 102a opens first, and the second valve port 102b is simultaneously open.
  • the first valve port 102a, the second valve port 102b, and the inner cavity 101 of the valve body 100 are connected.
  • the pressure of the old high-pressure fluid in the first valve port 102a gradually decreases, and new high-pressure fluid flows in from the bottom of the second piston 230.
  • a pressure difference is formed between the high-pressure fluid and the fluid in the inner cavity 101.
  • the fluid pressure formed by this pressure difference acts on the piston assembly 200.
  • the sum of the fluid pressure and the elastic force of a pair of first elastic elements 310 pushes the piston assembly 200 to its equilibrium position.
  • the direction of the fluid pressure is the same as the direction of the sum of the elastic forces of the pair of first elastic elements 310.
  • the direction of the fluid pressure is opposite to the direction of the sum of the elastic forces of the pair of first elastic elements 310.
  • the piston assembly 200 needs to overcome the sum of the elastic forces of the pair of first elastic elements 310 to move to the closed state of the second valve port 102b. Therefore, the sum of the elastic forces of the pair of first elastic elements 310 acts both as the driving force for opening the first valve port 102a and as the resistance for closing the second valve port 102b. Since the sum of the maximum elastic forces of the pair of first elastic elements 310 corresponding to curves 1, 2, and 3 is equal, this disclosure analyzes the elastic forces that the switching valve needs to overcome during switching.
  • the switching valve of this embodiment further includes a pair of second elastic elements 320 for keeping the piston assembly 200 in a balanced state.
  • the second elastic element 320 is a compression spring and is sleeved on the outer periphery of the plug rod 210.
  • a pair of second elastic members 320 are respectively located on both sides of the partition 110 along the movement direction of the piston assembly 200; further, one end of the pair of second elastic members 320 abuts against the guide sleeve 112, and the other end abuts against the first piston 220 and the second piston 230, respectively; further still, the guide sleeve 112 has a first limiting surface 1121 and a second limiting surface 1122, the first limiting surface 1121 and the second limiting surface 1122 being arranged opposite to each other along the axial direction of the piston rod 210; one end of the pair of second elastic members 320 abuts against the first limiting surface 1121 and the second limiting surface 1122, respectively.
  • the first elastic member 310 is sleeved on the outer periphery of the second elastic member 320.
  • the end of the first segment 112a facing away from the second segment 112b has a first limiting surface 1121, and the end of the second segment 112b facing away from the first segment 112a has a second limiting surface 1122.
  • the second elastic force provided by the second elastic member 320 to the piston assembly 200 is greater than the first elastic force provided by the first elastic member 310 to the piston assembly 200.
  • the lengths of a pair of second elastic members 320 are L3 and L4, respectively, where L3 is greater than L4.
  • the free length of the second elastic member 320 is L”, where L4 ⁇ L” ⁇ (L3 + L4)/2, and L’ ⁇ L1.
  • L can be less than L’.
  • curve 2 (L2 ⁇ L’ ⁇ (L1+L2)/2) contains a stroke where the elastic resultant force is zero (e.g., the horizontal axis 40% ⁇ 60%).
  • the piston assembly 200 is prone to instability and up-and-down swaying due to the zero elastic resultant force, resulting in noise and vibration.
  • L’ ⁇ L1 the piston assembly 200 is always in contact with a pair of second elastic elements 320, which support the piston assembly 200, ensuring stable operation throughout the process without swaying.
  • the switching valve in this embodiment is provided with a pair of first elastic elements 310 and a pair of second elastic elements 320.
  • the free length of the first elastic element 310 is designed to be L’ ⁇ L1
  • the free length of the second elastic element 320 is designed to be L4 ⁇ L” ⁇ (L3+L4)/2.
  • the elastic resultant force of the pair of first elastic elements 310 and the pair of second elastic elements 320 forms two curves respectively in the entire stroke of the piston assembly 200. The two curves are coupled to form the curve shown in Figure 16.
  • the maximum elastic resultant force on the piston assembly 200 in the entire stroke of Figure 16 is equal to the maximum elastic force on the piston assembly 200 in the entire stroke of Figure 4.
  • the second elastic force provided by the second elastic element to the piston assembly is greater than the first elastic force provided by the first elastic element to the piston assembly, causing the piston assembly 200 to move towards the equilibrium position under the action of the larger second elastic force. That is, the second elastic element with a larger elastic force effectively improves the valve's action capability, and the larger elastic force of the second elastic element can smoothly open the first valve port 102a.
  • the switching valve of this embodiment can simultaneously improve the valve's operating capability and prevent noise and vibration from the piston assembly 200.
  • the switching valve of this embodiment includes a valve body 100, a piston assembly 200, and elastic elements, the elastic elements including a pair of first elastic elements 310.
  • the valve body 100 has an inner cavity 101, with a first channel 102 and a second channel 103.
  • the piston assembly 200 is movably disposed within the inner cavity 101 for blocking the first channel 102 and/or the second channel 103; wherein the first channel 102 and the second channel 103 are arranged along the direction of movement of the piston assembly 200.
  • the elastic elements are used to keep the piston assembly 200 in a balanced state. When the piston assembly 200 is in a balanced state, it simultaneously blocks the first channel 102 and the second channel 103.
  • both the first channel 102 and the second channel 103 are closed.
  • the fluid driving force applied to the piston assembly 200 due to throttling is at its maximum when fluid passes through the switching valve, thus maximizing the switching valve's operational capability and improving its reliability.
  • the piston assembly can be switched from a state where the first channel 102 is blocked and the second channel 103 is open to a state where the second channel 103 is blocked and the first channel 102 is open.
  • the forces driving the piston assembly 200 are the elastic element and the fluid force.
  • the elastic element includes a pair of first elastic elements 310.
  • the pair of first elastic elements 310 are defined as a first elastic portion 310a and a second elastic portion 310b, respectively. The pair of first elastic elements 310 ensures the stability of the piston assembly 200 in a balanced state.
  • first elastic portion 310a is used to provide a first elastic force to the piston assembly 200 to move toward a position blocking the second channel 103; the second elastic portion 310b is used to provide a second elastic force to the piston assembly 200 to move toward a position blocking the first channel 102.
  • the inner cavity 101 is provided with a partition 110, which divides the inner cavity 101 into a first channel 102 and a second channel 103; the first elastic part 310a is located in the first channel 102 and the second elastic part 310b is located in the second channel 103.
  • the piston assembly 200 includes a piston rod 210, a first piston 220, and a second piston 230.
  • the first piston 220 is connected to one axial end of the piston rod 210 and is used to block the first channel 102.
  • One end of the first elastic part 310a abuts against the partition part 110, and the other end abuts against the first piston 220.
  • the second piston 230 is connected to the other axial end of the piston rod 210 and is used to block the second channel 103.
  • One end of the second elastic part 310b abuts against the partition part 110, and the other end abuts against the second piston 230.
  • one end of the first elastic portion 310a abuts against the partition portion 110, and the other end abuts against the first piston 220.
  • the first elastic force provided by the first elastic portion 310a is used to make the first piston 220 tend to open the first channel 102.
  • One end of the second elastic portion 310b abuts against the partition portion 110, and the other end abuts against the second piston 230.
  • the second elastic force provided by the second elastic portion 310b is used to make the second piston 230 tend to open the second channel 103.
  • first elastic part 310a and the second elastic part 310b can be compression springs and are sleeved on the outer periphery of the plug rod 210.
  • the first piston 220 includes a first body 221 and a first sealing ring 222.
  • the first body 221 is connected to one axial end of the piston rod 210, and the first sealing ring 222 is sleeved on the outer periphery of the first body 221 for sealing engagement with the first channel 102.
  • the first body 221 and the piston rod 210 can be connected by means of screwing, interference fit, welding, etc.
  • the second piston 230 includes a second body 231 and a second sealing ring 232.
  • the second body 231 is connected to the other axial end of the piston rod 210, and the second sealing ring 232 is sleeved on the outer periphery of the second body 231 for sealing engagement with the second channel 103.
  • the second body 231 and the piston rod 210 can be connected by means of screwing, interference fit, welding, etc.
  • the partition 110 includes a partition ring 111 and a guide sleeve 112.
  • the partition ring 111 is fixedly connected to the cavity wall of the inner cavity 101 and surrounds the outer periphery of the guide sleeve 112.
  • the plug rod 210 is movably inserted into the guide sleeve 112.
  • the stopper 210 is guided and engaged with the guide sleeve 112, which improves the stability of the movement of the stopper 210 and thus improves the reliability of the valve operation.
  • the guide sleeve 112 has a first limiting surface 1121 and a second limiting surface 1122 at both axial ends, which are arranged opposite to each other along the movement direction of the piston assembly 200.
  • the first limiting surface 1121 is configured to abut against the first piston 220 of the piston assembly 200 when the piston assembly 200 blocks the first channel 102 and moves to the first extreme position.
  • the second limiting surface 1122 is configured to abut against the second piston 230 of the piston assembly 200 when the piston assembly 200 blocks the second channel 103 and moves to the second extreme position.
  • the piston assembly 200 can be limited when it is in the first extreme position and the second extreme position.
  • the separator ring 111 has a first annular surface 1111 and a second annular surface 1112, which are arranged opposite to each other along the movement direction of the piston assembly 200; the portion of the guide sleeve 112 extending out of the first annular surface 1111 is defined as the first segment 112a, and the first elastic part 310a is sleeved on the outer periphery of the first segment 112a; the portion of the guide sleeve 112 extending out of the second annular surface 1112 is defined as the second segment 112b, and the second elastic part 310b is sleeved on the outer periphery of the second segment 112b.
  • the switching valve of this embodiment includes a valve body 10c and a piston assembly 20c.
  • the valve body 10c includes an inner cavity 11c, which has a first valve port 101c and a second valve port 102c.
  • the piston assembly 20c is movably disposed within the inner cavity 11c and includes a piston rod 21c, a first piston 22c, and a second piston 23c.
  • the first piston 22c and the second piston 23c are respectively connected to opposite ends of the piston rod 21c.
  • the first valve port 101c and the second valve port 102c are arranged at intervals along the movement direction of the piston assembly 20c.
  • the first piston 22c is used to block the first valve port 101c
  • the second piston 23c is used to block the second valve port 102c.
  • At least one of the first piston 22c and the second piston 23c is injection molded.
  • the switching valve disclosed herein helps control the weight and cost of the switching valve. Furthermore, during the movement of the piston assembly 20c within the inner cavity 11c, the injection-molded first piston 22c and/or second piston 23c can reduce abnormal noise from friction and impact with the inner wall of the inner cavity 11c and between the first valve port 101c and the second valve port 102c, thereby improving the quietness of the switching valve.
  • the valve body 10c may include a valve seat 12c and a valve cover 13c.
  • the valve seat 12c has an inner cavity 11c, and the valve cover 13c is connected to the valve seat 12c.
  • the valve cover 13c is made of metal, and the valve seat 12c can be made of metal or plastic.
  • the plastic valve seat 12c is lightweight and helps to save costs.
  • the valve cover 13c has a through first opening 131c, which communicates with the inner cavity 11c
  • the valve seat 12c has a through second opening 121c, which communicates with the inner cavity 11c.
  • the first opening 131c can serve as a fluid inlet of the switching valve, which can communicate with the compressor outlet.
  • the second opening 121c can serve as a fluid outlet of the switching valve, which can communicate with the compressor inlet.
  • the end of the valve seat 12c away from the valve cover 13c can serve as another fluid inlet of the switching valve, which can communicate with the compressor inlet; when the first piston 22c blocks the first valve port 101c, the second opening 121c communicates with this fluid inlet.
  • the switching valve disclosed herein can be a three-way valve, including two fluid inlets and one fluid outlet.
  • valve seat 12c has a through first opening 131c, which communicates with the inner cavity 11c, and valve seat 12c has a through second opening 121c, which also communicates with the inner cavity 11c. That is, both the first opening 131c and the second opening 121c are located on valve seat 12c.
  • the valve seat 12c has a third opening 122c, which is radially arranged along the valve seat 12c and communicates with the inner cavity 11c; a portion of the valve cover 13c extends into the third opening 122c, or the valve cover 13c is sleeved outside the third opening 122c.
  • a riveting portion is provided at one end of the valve seat 12c with the third opening 122c, and the riveting portion is connected to the valve cover 13c.
  • the valve cover 13c has a riveting portion at one end near the valve seat 12c, and the riveting portion is connected to the valve seat 12c.
  • the valve cover 13c has a fitting section 132c extending into the third opening 122c, the outer peripheral surface of the fitting section 132c being press-fitted with the inner peripheral surface of the third opening 122c.
  • the outer diameter of the fitting section 132c before the valve cover 13c is fitted with the valve seat 12c is larger than the outer diameter of the fitting section 132c after the valve cover 13c is fitted with the valve seat 12c.
  • the valve cover 13c has a fitting section 132c sleeved outside the third opening 122c, the inner peripheral surface of the fitting section 132c being press-fitted with the outer peripheral surface of the valve seat where the third opening 122c is located.
  • valve cover 13c and the valve seat 12c can also be connected by a threaded connection or welded together.
  • the valve cover 13c and the valve seat 12c can be integrally formed.
  • the elastic member includes a first elastic portion 31c and a second elastic portion 32c.
  • the inner cavity 11c is provided with a partition portion 125c that separates the first valve port 101c and the second valve port 102c.
  • the first elastic portion 31c is sleeved on the stopper rod 21c and is located between the first piston 22c and the partition portion 125c. The opposite ends of the first elastic portion 31c abut against the first piston 22c and the partition portion 125c, respectively.
  • the second elastic portion 32c is sleeved on the stopper rod 21c and is located between the second piston 23c and the partition portion 125c. The opposite ends of the second elastic portion 32c abut against the second piston 23c and the partition portion 125c, respectively.
  • the first elastic part 31c can be a compression spring
  • the second elastic part 32c can be a compression spring
  • the valve seat 12c includes a first valve sleeve 123c and a second valve sleeve 124c coaxially arranged and connected.
  • the valve cover 13c is connected to the first valve sleeve 123c
  • the second valve sleeve 124c is connected to the first valve sleeve 123c.
  • the two ends of the second valve sleeve 124c form a first valve port 101c and a second valve port 102c, respectively.
  • the first valve sleeve 123c and the second valve sleeve 124c can be integrally formed.
  • a first opening 131c can be provided on the peripheral sidewall of the first valve sleeve 123c, and a second opening 121c can be provided on the second valve sleeve 124c.
  • the valve seat 12c may not include the first valve sleeve 123c but may have a second valve sleeve 124c, and the first opening 131c may be provided on the valve cover 13c.
  • the valve seat 12c may further include a third valve sleeve, which is coaxially disposed with and connected to the side of the second valve sleeve 124c away from the first valve sleeve 123c.
  • the first valve sleeve 123c, the second valve sleeve 124c, and the third valve sleeve may be integrally formed.
  • the fluid inlet at the end of the valve seat 12c away from the valve cover 13c may be disposed on the peripheral sidewall of the third valve sleeve.
  • the maximum value of the outer diameter of the second valve sleeve 124c is less than the maximum value of the outer diameter of the first valve sleeve 123c.
  • the maximum value of the outer diameter of the second valve sleeve 124c may be less than the maximum value of the outer diameter of the first valve sleeve 123c, and the maximum value of the outer diameter of the third valve sleeve may also be less than the maximum value of the outer diameter of the first valve sleeve 123c.
  • the first piston 22c includes a first body 221c and a first sealing ring 222c sleeved on the outer periphery of the first body 221c.
  • first sealing ring 222c is compressed between the first body 221c and the first valve port 101c to seal the first valve port 101c.
  • the second piston 23c includes a second body 231c and a second sealing ring 232c sleeved on the outer periphery of the second body 231c.
  • the phrase "at least one of the first piston 22c and the second piston 23c is injection molded" in this disclosure refers to at least one of the first body 221c and the second body 231c being injection molded, and does not mean that the first sealing ring 222c is also injection molded with the first body 221c, or that the second sealing ring 232c is also injection molded with the second body 231c.
  • the valve body 10c has a first end face 1241c, and preferably the second valve sleeve 124c also has a first end face 1241c.
  • the first end face 1241c is located at the end of the first valve port 101c near the valve cover 13c.
  • the first piston 22c has a first limiting surface 223c, which abuts against the first end face 1241c when the first piston 22c blocks the first valve port 101c.
  • the first limiting surface 223c abuts against the first end face 1241c, the first piston 22c moves to its limit position towards the first valve port 101c, and the first body 221c and the compressed first sealing ring 222c seal the first valve port 101c.
  • the valve body 10c has a second end face 1242c, and preferably the second valve sleeve 124c has a second end face 1242c.
  • the second end face 1242c is located at the end of the second valve port 102c away from the valve cover 13c.
  • the second piston 23c has a second limiting surface 233c, which abuts against the second end face 1242c when the second piston 23c blocks the second valve port 102c.
  • the second piston 23c moves to its limit position towards the second valve port 102c, and the second body 231c and the compressed second sealing ring 232c seal the second valve port 102c.
  • the stopper rod 21c may include a metallic material; for example, the stopper rod 21c may not include non-metallic materials.
  • the first piston 22c may be made of plastic.
  • the first piston 22c may be integrally injection molded with the stopper rod 21c as a metal insert.
  • the second piston 23c may include a metallic material, be formed by machining, and be mechanically connected to the stopper rod 21c.
  • the second piston 23c may also be made of the same metallic material as the stopper rod 21c.
  • the second piston 23c may be made of plastic.
  • the piston rod 21c may be made of plastic, and the first piston 22c may also be made of plastic.
  • the piston rod 21c can be integrally injection molded with the first piston 22c.
  • the second piston 23c may include a metal material, formed by machining, and can be mechanically connected to the piston rod 21c.
  • both the first piston 22c and the second piston 23c may be made of plastic.
  • both the valve cover 13c and the stopper rod 21c can be made of aluminum alloy.
  • the valve seat 12c is injection molded from plastic.
  • the valve cover 13c and the valve seat 12c can be riveted or connected by an interference fit.
  • the forming and connection methods of the stopper rod 21c, the first body 221c, and the second body 231c can refer to the aforementioned embodiments.
  • the first opening 131c can be provided on the valve seat 12c, specifically on the first valve sleeve 123c, thereby relatively shortening the length of the valve cover 13c and facilitating the metal machining of the valve cover 13c.
  • the valve cover 13c is made of a metal material, such as aluminum alloy.
  • the valve seat 12c is injection molded from plastic, and the valve cover 13c and the valve seat 12c can be riveted or connected by an interference fit.
  • the stopper rod 21c is made of a metal material, such as aluminum alloy.
  • the first piston 22c can be made of plastic and is integrally injection molded with the stopper rod 21c as an insert.
  • the second piston 23c is made of metal, formed by machining, and can be mechanically connected to the stopper rod 21c.
  • the second piston 23c can be made of plastic, integrally injection molded with the stopper rod 21c as an insert, and the first piston 22c is made of metal, formed by machining, and can be mechanically connected to the stopper rod 21c.
  • the first opening 131c can be located on the valve seat 12c, specifically on the first valve sleeve 123c, thereby allowing the length of the valve cover 13c to be relatively shortened, facilitating the metal machining of the valve cover 13c.
  • a throttling channel is formed between the piston assembly 20c and the valve port.
  • the ratio of the maximum flow area of the throttling channel to the maximum flow area of the valve port is ⁇ 3/10.
  • the throttling channel ensures that the fluid continuously exerts a significant driving force on the piston assembly 20c from its equilibrium state until the valve port is fully closed, which is beneficial for improving the switching valve's actuation capability.
  • the throttling channel includes a first throttling channel 111c, which is formed between the outer peripheral surface of the first piston 22c and the first valve port 101c.
  • the ratio of the maximum flow area of the first throttling channel 111c to the maximum flow area of the first valve port 101c is ⁇ 3/10.
  • the throttling channel may also include a second throttling channel 112c, which is formed between the outer peripheral surface of the second piston 23c and the second valve port 102c.
  • the ratio of the maximum flow area of the second throttling channel 112c to the maximum flow area of the second valve port 102c is ⁇ 3/10.
  • the first throttling channel 111c and the second throttling channel 112c can improve the operating capability of the switching valve and reduce the operating pressure differential.
  • the first valve port 101c has an inner conical surface that contracts towards the second valve sleeve 124c.
  • the inner conical surface can form the inner wall of the first throttling channel 111c.
  • the flow area of the first throttling channel 111c gradually decreases.
  • the fluid force generated by throttling gradually increases as the first piston 22c gradually blocks the first valve port 101c, and the elastic force of the first elastic part 31c gradually increases.
  • the second valve port 102c also has an inner conical surface, and the inner conical surface contracts towards the second valve sleeve 124c.
  • the inner conical surface can form a second throttling channel 112c.
  • the flow area of the second throttling channel 112c gradually decreases, and the fluid force generated by throttling gradually increases as the second piston 23c gradually blocks the second valve port 102c.
  • the valve body 10c is installed as a cartridge valve into a mounting base (not shown in the figure).
  • a limiting platform is provided on the outside of the valve body 10c, and a threaded connection portion is provided on the outer periphery of the valve body 10c, which is threadedly connected to the mounting base.
  • the limiting platform abuts against the mounting base.
  • the limiting platform and the threaded connection portion together limit the movement of the valve body 10c; the limiting platform prevents the valve body 10c from moving downwards, and the threaded connection portion prevents the valve body from moving upwards.
  • this disclosure also provides a refrigeration system including the switching valve of any of the above embodiments. Since the refrigeration system of this disclosure includes the switching valve of any of the above embodiments, it possesses all the advantages and beneficial effects of any of the above embodiments, which will not be elaborated further here.
  • the terms “first,” “second,” and “third” are used for descriptive purposes only and should not be construed as indicating or implying relative importance; the term “multiple” refers to two or more unless otherwise expressly defined.
  • the terms “install,” “connect,” “link,” and “fix” should be interpreted broadly. For example, “connect” can be a fixed connection, a detachable connection, or an integral connection; “link” can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this application based on the specific circumstances.
  • the terms “one embodiment,” “some embodiments,” “specific embodiment,” etc. refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the claims.
  • the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example.
  • the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

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Abstract

切换阀包括阀体（100）、活塞组件（200）和弹性件，阀体（100）包括具有阀口的内腔（101）；活塞组件（200）可动地设于内腔（101）内，用于封堵或打开阀口；弹性件用于使活塞组件（200）处于平衡状态；平衡状态是指：在无流体冲击下，活塞组件相（200）对于阀体（100）保持不动；活塞组件（200）与内腔（101）的腔壁之间形成与阀口连通的节流通道；其中，活塞组件（200）处于平衡状态时，节流通道的最大流通面积与阀口最大流通面积的比值≤3/10。

Description

切换阀
交叉引用
本公开要求于2024年7月31日提交的申请号为202411047213.X、名称为“切换阀及制冷系统”，申请号为202421834340.X、名称为“切换阀及制冷系统”，申请号为202421841966.3、名称为“切换阀及制冷系统”，以及2024年11月20日提交的申请号为202422838717.5、名称为“切换阀”的中国专利申请的优先权，四件中国专利申请的全部内容通过引用全部并入本文。
技术领域
本公开涉及流体控制技术领域，具体而言，涉及一种切换阀。
背景技术
相关技术中的切换阀在流体压力的驱动下，可在阀体的阀腔内运动。如流体作用于切换阀的压力较小，将使得切换阀动作能力不高，有时甚至会出现阀门无法完全关闭或完全开启，影响阀门的可靠性。
发明内容
本公开提供一种切换阀，包括阀体、活塞组件和弹性件，阀体包括具有阀口的内腔；活塞组件可动地设于内腔内，用于封堵或打开阀口；弹性件用于使活塞组件处于平衡状态；平衡状态是指：在无流体冲击下，活塞组件相对于阀体保持不动；活塞组件与内腔的腔壁之间形成与阀口连通的节流通道；其中，活塞组件处于平衡状态时，节流通道的最大流通面积与阀口最大流通面积的比值≤3/10。
附图说明
图1示出的是本公开第一实施例的切换阀的分解示意图。
图2示出的是本公开第一实施例的切换阀的俯视示意图。
图3示出的是沿图2中A-A剖切线的剖视图。
图4示出的是活塞组件处于平衡状态时，节流通道的最大流通面积与阀口最大流通面积的比值＞3/10时，切换阀的流通面积曲线图。
图5示出的是活塞组件处于平衡状态时，节流通道的最大流通面积与阀口最大流通面积的比值≤3/10时，切换阀的流通面积曲线图。
图6示出的是活塞组件处于平衡状态时，节流通道的最大流通面积与阀口最大流通面积的比值＞3/10时，切换阀的流阻曲线图。
图7示出的是活塞组件处于平衡状态时，节流通道的最大流通面积与阀口最大流通面积的比值≤3/10时，切换阀的流阻曲线图。
图8示出的是本公开第二实施例的切换阀的剖视图。
图9示出的是本公开第三实施例的切换阀的剖视图。
图10示出的是本公开第四实施例的切换阀的剖视图。
图11示出的是本公开第五实施例的切换阀的剖视图。
图12示出的是本公开第五实施例的切换阀的活塞组件的立体示意图。
图13示出的是本公开第六实施例的切换阀的分解示意图。
图14示出的是本公开第六实施例的切换阀的剖视图。
图15示出的是本公开第六实施例的切换阀中第一弹性件的自由长度处于三个不同区间时，一对第一弹性件施加在活塞组件上的弹性合力的曲线示意图。
图16示出的是一对第一弹性件和一对第二弹性件同时作用于活塞组件时的弹性合力的曲线示意图。
图17示出的是本公开第七实施例的切换阀的分解示意图。
图18示出的是本公开第七实施例的切换阀的剖视图。
图19示出的是本公开第八实施例的切换阀的一种示例性实施方式的分解示意图；
图20示出的是本公开第八实施例的切换阀的一种示例性实施方式的沿塞杆纵向剖切示意图；
图21示出的是本公开第八实施例的切换阀的另一种示例性实施方式的沿塞杆纵向剖切示意图；
图22示出的是本公开第八实施例的切换阀的一种示例性实施方式中活塞组件的示意图；
图23示出的是本公开第八实施例的切换阀的一种示例性实施方式中阀体的示意图。
具体实施方式
现在将参考附图更全面地描述示例实施方式。然而，示例实施方式能够以多种形式实施，且不应被理解为限于在此阐述的实施方式；相反，提供这些实施方式使得本公开将全面和完整，并将示例实施方式的构思全面地传达给本领域的技术人员。图中相同的附图标记表示相同或类似的结构，因而将省略它们的详细描述。
可以理解的是，本公开实施例中的术语“包括”和“具有”以及它们任何变形，意图在于覆盖不排他的包含。例如包含了一系列步骤或单元的过程、方法、系统、产品或设备没有限定于已列出的步骤或单元，而是可选地还包括没有列出的步骤或单元，或可选地还包括对于这些过程、方法、产品或设备固有的其它步骤或组件。
【实施例一】
如图1至图3所示，本公开实施例的切换阀包括阀体100、活塞组件200和弹性件。阀体100包括具有阀口(102a,102b)的内腔101；活塞组件200可动地设于内腔101内，用于封堵或打开阀口；弹性件用于使活塞组件200处于平衡状态；其中，活塞组件200处于平衡状态时，活塞组件200与内腔101的腔壁之间形成与阀口连通的节流通道。节流通道的最大流通面积与阀口的最大流通面积的比值≤3/10，可使活塞组件从处于平衡状态至阀口完全关闭范围内，流体一直可对活塞组件产生较大的驱动力，有利于提高切换阀的动作能力。
其中，阀口包括第一阀口102a和第二阀口102b，第一阀口102a和第二阀口102b沿活塞组件200的运动方向上间隔布置。活塞组件200用于分别封堵第一阀口102a和第二阀口102b。第一阀口102a的最大流通面积为S11，第二阀口102b的最大流通面积为S12。
阀口最大流通面积是指阀口完全打开时的流体流通截面积，即阀口的开口面积。节流通道的流通面积是指流通面积的开口面积。
弹性件包括一对第一弹性件310，一对第一弹性件310分别定义为第一弹性部310a和第二弹性部310b。第一弹性部310a和第二弹性部310b用于保持活塞组件在平衡状态时的稳定性。并且第一弹性部310a用于向活塞组件200提供朝着封堵第二阀口102b的位置移动的第一弹性力，第二弹性部310b用于向活塞组件200提供朝着封堵第一阀口102a的位置移动的第二弹性力。
在一实施方式中，活塞组件200处于平衡状态时，第一弹性部310a和第二弹性部310b作用于活塞组件200的弹力与活塞组件200的重力的合力为零。
如图1和图3所示，阀体100可以包括阀座120和阀盖130，阀座120具有内腔101，阀盖130连接于阀座120。其中，本公开对阀盖130与阀座120的连接方式不作限定，例如螺纹连接、焊接、过盈配合等。或阀盖130与阀座120一体设置。
阀盖130具有第一开口131，第一开口131与内腔101连通。阀座120具有第二开口121，第二开口121与内腔101连通。其中，活塞组件200封堵第一阀口102a时，第一开口131与第二开口121不连通；活塞组件200封堵第二阀口102b时，第一开口131与第二开口121连通。第一开口131可作为切换阀发流体进口，与压缩机的出口连通。第二开口121可作为切换阀的流体出口，与压缩机的进口连通。阀座120的远离阀盖130的一端可作为切换阀流体的另一进口，可与压缩机的出口连通。因此，切换阀可为三通阀，包括两处流体进口，一处流体出口。
如图3所示，活塞组件200包括塞杆210、第一活塞220和第二活塞230。第一活塞220连接于塞杆210的一端，用于封堵第一阀口102a。第二活塞230连接于塞杆210的另一端，用于封堵第二阀口102b。
在一实施方式中，第一弹性部310a、第二弹性部310b为压簧，且套设于塞杆210的外周。
如图3所示，阀座120包括两个第一阀套122和连接于两个第一阀套122之间的第二阀套123，第一阀套122、第二阀套123同轴设置。第二阀套123的两端分别形成第一阀口102a和第二阀口102b。
其中，活塞组件200封堵第一阀口102a时，其中一个第一阀套122套设于第一活塞220的外周；活塞组件200封堵第二阀口102b时，另一个第一阀套122套设于第二活塞230的外周。
当然，在其他实施例中，阀座120也可以不包括第一阀套122而具有第二阀套123。
如图3所示，内腔101内设有分隔部110，分隔部110将第一阀口102a和第二阀口102b隔开；第一弹性部310a位于第一活塞220和分隔部110之间，且第一弹性部310a的一端与分隔部110抵接，另一端与第一活塞220抵接。第二弹性部310b位于第二活塞230和分隔部110之间，且第二弹性部310b的一端与分隔部110抵接，另一端与第二活塞230抵接。
在一实施方式中，分隔部110包括分隔环111和导向套112，分隔环111固定连接于第二阀套123的内周面，且环绕连接于导向套112的外周，导向套112具有导向孔110a，塞杆210可动地穿设于导向套112的导向孔110a内。
于本公开实施例中，塞杆210与导向套112导向配合，提高了塞杆210运动的稳定性，进而提高了阀动作的可靠性。
在其他实施例中，分隔部110也可以包括分隔环111，分隔环111围成导向孔110a。
如图3所示，分隔环111具有第一环面1111和第二环面1112，第一环面1111和第二环面1112沿活塞组件200的运动方向相背设置；导向套112伸出于第一环面1111的部分定义为第一段112a，第一弹性部310a套设于第一段112a的外周；导向套112伸出于第二环面1112的部分定义为第二段112b，第二弹性部310b套设于第二段112b的外周。
如图3所示，节流通道包括与第一阀口102a连通的第一节流通道410以及与第二阀口102b连通的第二节流通道420，第一节流通道410的最大流通面积为S21，第二节流通道420的最大流通面积为S22；活塞组件200处于平衡状态时，S21/S11≤3/10，S22/S12≤3/10。
于本公开实施例中，第一节流通道410形成于第一活塞220的外周面与其中一个第一阀套122的内周面之间，第二节流通道420形成于第二活塞230的外周面与另一个第一阀套122的内周面之间。
活塞组件200由阀口流通面积为零运动至阀口为最大流通面积时，行程为S1；活塞组件200位于阀口流通面积为零至阀口为最大流通面积之间时，行程为S2，阀口可以为第一阀口102a或第二阀口102b。图4和图5中的横坐标表示切换阀的S2/S1的值，即开度。图4和图5中的纵坐标表示切换阀处于不同开度时所对应的阀口流通面积与阀口最大流通面积的比值。流体经活塞组件200与阀座120内壁之间的开口流入阀口，在开口面积未达到阀口开口面积之前，阀口流通面积等于活塞组件200与阀座120内壁之间的开口面积。随着活塞组件200运动，当活塞组件200与阀座120内壁之间的开口面积减少到一定程度时，活塞组件200与阀座120内壁之间的开口面积即为本实施例的节流通道面积。
高压流体经过节流通道进入阀口，流体经节流通道节流后变成低压流体，低压流体从第二开口121流出，活塞组件200受到阀口前后的流体压差力。或者高压流体直接进入阀口内的节流通道后变成低压流体，低压流体从第二开口121流出，活塞组件200受到阀口前后的流体压差力。活塞组件200在阀口流通面积为零时，受到阀口前后的流体压差为F1。活塞组件200在阀口流通面积为零至阀口为最大流通面积之间时，受到阀口前后的流体压差为F2。图6和图7中的横坐标表示切换阀的开度。图6和图7中的纵坐标表示切换阀处于不同开度时所对应的F2/F1的值。
为了方便说明，下述关于图4至图7的描述中均以第一阀口102a为例，例如图4至图7的横坐标中的0％表示活塞组件200封堵第一阀口102a时，活塞组件200所处位置；横坐标中的100％表示第一阀口102a完全打开时，活塞组件200所处位置。
图4、图6中，活塞组件200处于所述平衡状态时，节流通道的最大流通面积与所述阀口最大流通面积的比值＞3/10。由图4可以看出，当第一阀口102a由关闭状态向完全打开状态切换的过程中，流通面积随着开度的增大而逐渐稳步增大，当活塞组件200的开度达到50％时，节流通道的流通面积小于阀口最大流通面积，此时阀口流通面积等于节流通道的流通面积，阀口流通面积与阀口最大流通面积的比值略高于60％，而此时F2/F1的值在25％左右。
图5、图7中，活塞组件200处于所述平衡状态时，节流通道的最大流通面积与所述阀口最大流通面积的比值≤3/10。由图5可以看出，当第一阀口102a由关闭状态向完全打开状态切换的过程中，在活塞组件200的开度达到50％的范围内，阀口流通面积随着开阀行程的增大而基本不变，当活塞组件200的开度达到55％时，节流通道的流通面积小于阀口最大流通面积，此时阀口流通面积等于节流通道的流通面积，阀口流通面积与阀口最大流通面积的比值在8％左右，而此时F2/F1的值在95％左右。因此，可明显看出，活塞组件200的开度达到55％的范围内，活塞组件200均受到阀口前后的加大的流体压差驱动力，有利于提高阀的动作能力，流体压差驱动力不仅能够克服弹性件施加给活塞组件200的弹力，同时还使活塞组件200快速进行不同工况的切换。当进行第一阀口102a的关闭操作时，活塞组件200运行至平衡状态时，可具有较大的流体压差驱动力，流体压差驱动力保证了第一阀口102a的顺利关闭。
如图5所示，由于第一活塞220的外周面与第一阀套122的内周面之间形成第一节流通道410，且S21/S11≤3/10，因此在开度0％～55％区间内，切换阀的第一阀口102a流通面积较小。当开阀行程处于55％～100％时，切换阀的第一阀口102a流通面积逐渐变大。在开度0％～55％区间内产生较大的流体压差驱动力。
由图6可以看出，第一阀口102a由关闭状态向完全打开状态切换的过程中，F2很快逐渐变小，这不利于提高阀的动作能力。
由图7可以看出，由于第一活塞220的外周面与第一阀套122的内周面之间形成第一节流通道410，且S21/S11≤3/10，因此在开度在0％～55％区间内，F2保持在较大值，当开度处于55％～100％时，F2才逐渐变小，有利于推动活塞组件200由平衡状态至完全关闭状态。
由此可见，本公开实施例的切换阀，活塞组件200与内腔101的腔壁之间形成与阀口连通的节流通道，活塞组件200处于平衡状态时，节流通道的最大流通面积与阀口的最大流通面积的比值≤3/10。因此在切换阀执行切换动作时，在一定开阀行程内，切换阀所受流阻可维持较大值，有利于提高切换阀的动作能力，降低动作压差。
【实施例二】
如图8所示，本公开第二实施例与第一实施例的相同之处不再赘述，其不同之处在于：
活塞组件200处于平衡状态时，节流通道还包括与第一阀口102a连通的第三节流通道430以及与第二阀口102b连通的第四节流通道440，第三节流通道430的最大流通面积为S31，第四节流通道440的最大流通面积为S32。S31/S11≤3/10，S32/S12≤3/10。
第一活塞220、第二活塞230均具有插入部240。活塞组件200处于平衡状态时，第一活塞220的插入部240伸入第一阀口102a内，且第一活塞220的插入部240的外周面与第一阀口102a的孔壁之间形成第三节流通道430，第二活塞230的插入部240伸入第二阀口102b内，且第二活塞230的插入部240与第二阀口102b的孔壁之间形成第四节流通道440。
于本公开实施例中，活塞组件200处于平衡状态时，不仅设置有第一节流通道410和第二节流通道420，而且还设置有第三节流通道430和第四节流通道440，进一步提高了切换阀的动作能力。
当然，可以理解的是，在其他实施例中，切换阀也可以仅设置第三节流通道430、第四节流通道440，而不设置第一节流通道410、第二节流通道420。
【实施例三】
如图9所示，本公开第三实施例与第一实施例的相同之处不再赘述，其不同之处在于：
活塞组件200在封堵阀口的过程中，第一阀套122的内周面与活塞组件200之间形成的节流通道的流通面积逐渐变小。
于本公开实施例中，活塞组件200封堵第一阀口102a的过程中，第一节流通道410的流通面积逐渐变小，活塞组件200封堵第二阀口102b的过程中，第二节流通道420的流通面积逐渐变小。如此，节流产生的流体力随着活塞组件200逐渐封堵阀口而逐渐增大，第一弹性部310a的弹力随着活塞组件200逐渐封堵阀口而逐渐增大，这样可克服随着阀口关闭而逐渐增大的弹性力，以进一步提高阀动作能力。
如图9所示，第一阀套122的内周面具有内圆锥面1221。通过设置内圆锥面1221，不仅可以进一步提高阀动作能力，而且还能避免因节流通道过窄而造成活塞组件200卡死在第一阀套122。
【实施例四】
如图10所示，本公开第四实施例与第三实施例的相同之处不再赘述，其不同之处在于：
活塞组件200的第一活塞220的外周面、第二活塞230的外周面均具有第一外圆锥面250。
【实施例五】
如图11所示，本公开第五实施例与上述实施例的相同之处不再赘述，其不同之处在于：
活塞组件200包括塞杆210、第一活塞220和第二活塞230，第一活塞220和第二活塞230连接于塞杆210，且沿塞杆210的轴向间隔布置。阀体100具有导向部132，塞杆210与导向部132导向配合。于本公开实施例中，导向部132可引导塞杆210运动，进而避免塞杆210在运动中发生偏斜而影响活塞封堵阀口的密封性。导向配合是指塞杆210与导向部132之间具有较小的间隙。
在一实施方式中，阀体100包括阀盖130和阀座120，阀座120具有内腔101，阀盖130连接于阀座120。导向部132一体形成于阀盖130。
进一步地，第一活塞220靠近阀盖130设置，塞杆210具有导向段211，导向段211位于第一活塞220背向第二活塞230的一侧。导向段211与导向部132导向配合。
在一实施方式中，导向部132可以为孔，导向段211与孔的内壁面导向配合。
如图12所示，第一活塞220、第二活塞230均包括第一活塞片260、第二活塞片270和第三活塞片280。其中，第二活塞片270夹设于第一活塞片260和第三活塞片280之间。第二活塞片270可由橡胶材料制成，第一活塞片260和第三活塞片280可由金属材料制成。
其中，活塞封堵阀口时，第一活塞片260伸入阀口内。于本公开实施例中，第一活塞220封堵第一阀口102a时，第一活塞220的第一活塞片260伸入第一阀口102a内，第二活塞230位于第二阀口102b外部；第二活塞230封堵第二阀口102b时，第二活塞230的第一活塞片260伸入第二阀口102b内，第一活塞220位于第一阀口102a外部。
在一实施方式中，第二活塞片270具有与阀口密封配合的第二外圆锥面271。通过二外圆锥面271与阀口密封配合，可提高活塞封堵阀口的密封性。
如图12所示，第一活塞片260的外周面具有外圆柱面261和两个第三外锥面262，两个第三外锥面262对称连接于外圆柱面261沿活塞组件200的运动方向的两端。其中，外圆柱面261的直径略小于阀口的直径。
于本公开实施例中，第一活塞片260的外周面具有外圆柱面261和两个第三外锥面262，一方面，可避免在开阀/关阀过程中，第一活塞片260卡在阀口的边缘；另一方面，由于两个第三外锥面262对称连接于外圆柱面261沿活塞组件200的运动方向的两端，在组装第一活塞片260时，无需考虑第一活塞片260的正面或反面，提高了组装效率。
可以理解的是，本实施例中的导向部132、第二外圆锥面271、外圆柱面261和两个第三外锥面262适用于上述任一实施例的切换阀，此处不再一一列举。
【实施例六】
如图13和图14所示，本公开第六实施例与上述实施例的相同之处不再赘述，其不同之处在于：
本公开实施例的切换阀包括阀体100、活塞组件200和弹性件。弹性件可以包括一对第一弹性件310。一对第一弹性件310用于使活塞组件200处于平衡状态。
在一实施方式中，第一弹性件310为压簧，且套设于塞杆210的外周。
如14所示，内腔101内设有分隔部110，分隔部110将第一阀口102a和第二阀口102b隔开，且具有导向孔110a；塞杆210可动地穿设于导向孔110a内。其中一个第一弹性件310位于第一活塞220和分隔部110之间，且该其中一个第一弹性件310的一端与分隔部110抵接，另一端与第一活塞220抵接。另一个第一弹性件310位于第二活塞230和分隔部110之间，且该另一个第一弹性件310的一端与分隔部110抵接，另一端与第二活塞230抵接。
如图14所示，分隔环111具有第一环面1111和第二环面1112，第一环面1111和第二环面1112沿活塞组件200的运动方向相背设置；导向套112伸出于第一环面1111的部分定义为第一段112a，其中一个第一弹性件310套设于第一段112a的外周；导向套112伸出于第二环面1112的部分定义为第二段112b，另一个第一弹性件310套设于第二段112b的外周。
其中，活塞组件200封堵第一阀口102a、第二阀口102b其中一个时，一对第一弹性件310的长度分别为L1、L2，L1大于L2，第一弹性件310的自由长度为L’，L2<L’≤(L1+L2)/2，或L’≥L1。其中，“自由长度”是指弹簧两端没有被施加任何外力时的长度值。
如图15所示，示出了第一弹性件310的自由长度分别处于三个不同区间时，一对第一弹性件310施加在活塞组件200上的弹性合力的曲线示意图。三个不同区间分别为：L’≥L1(曲线1)、(L1+L2)/2<L'<L1(曲线2)、L2<L’≤(L1+L2)/2(曲线3)。
其中，图15的横坐标表示切换阀的开度，纵坐标表示切换阀处于不同开度时所对应的弹性合力与最大弹性合力的比值，最大弹性合力是指活塞组件200封堵第一阀口102a和第二阀口102b其中一个时，一对第一弹性件310施加在活塞组件200上的弹性合力。曲线1、曲线2以及曲线3对应的三对不同的第一弹性件310，施加给活塞组件200的最大弹性合力均相等，即曲线1、曲线2以及曲线3具有同一个起始点与同一个终点。
为了方便说明，以第一阀口102a为例，例如图15的横坐标中的0％表示活塞组件200封堵第一阀口102a、第二阀口102b完全打开时，活塞组件200所处位置；横坐标中的100％表示第一阀口102a完全打开、活塞组件200封堵第二阀口102b时，活塞组件200所处位置。其中，横坐标为50％时，表示活塞组件200处于平衡状态，即一对第一弹性件310施加在活塞组件200上的弹性合力为零。
需要说明的是，横坐标中0％～50％表示活塞组件200由第一位置(封堵第一阀口102a)移动至平衡状态，50％～100％表示活塞组件200由平衡状态移动至第二位置(封堵第二阀口102b)。
进行工况切换时，在横坐标0％的位置，第一阀口102a完全关闭，压缩机未停机，高压流体从第二活塞230的底部开始流入，此时第一阀口102a内的高压流体压力还未开始降低，此时推动活塞组件200开启第一阀口102a的力主要为一对第一弹性件310的弹力之和，一对第一弹性件310的弹力之和打开第一阀口102a，第一弹性件310的弹力之和越大，越能够瞬间打开第一阀口102a，即第一弹性件310的弹力大小是决定能否顺利开启第一阀口102a的关键因素；在横坐标0％～50％范围内，第一阀口102a先打开，第二阀口102b同时处于打开状态，第一阀口102a、第二阀口102b、阀体100的内腔101连通，第一阀口102a内的旧高压流体压力逐渐降低，新的高压流体从第二活塞230的底部流入，高压流体与内腔101的流体形成压强差，压强差形成的流体压力作用于活塞组件200，流体压力与一对第一弹性件310的弹力之和推动活塞组件200运动至平衡状态所在位置。流体压力的方向与一对第一弹性件310的弹力之和的方向相同。
之后，在横坐标50％～100％范围内，流体压力的方向与一对第一弹性件310的弹力之和的方向相反。活塞组件200需要克服一对第一弹性件310的弹力之和运动至第二阀口102b处于关闭状态。因此一对第一弹性件310的弹力之和既充当开启第一阀口102a的驱动力，又充当关闭第二阀口102b的阻力。因曲线1、曲线2以及曲线3对应的一对第一弹性件310的最大弹力之和均相等，本公开对切换阀在切换时需要克服的弹力进行分析。
由图15可以看出，在横坐标50％～100％范围内，三条曲线在同一横坐标值时，曲线1对应的弹性合力、曲线2对应的弹性合力均小于曲线3对应的弹性合力。由此可知，切换阀在切换时，曲线1中流阻需要克服的阻力、曲线2中流阻需要克服的阻力均小于曲线3中流阻需要克服的阻力。
因此，本公开实施例的切换阀，由于第一弹性件310的自由长度L’满足：L2<L’≤(L1+L2)/2，或L’≥L1，在阀切换时需要克服的阻力变小，进而有效提升了阀的动作能力。
如图14所示，本公开实施例的切换阀还包括一对第二弹性件320，用于使活塞组件200处于平衡状态。
在一实施方式中，第二弹性件320为压簧，且套设于塞杆210的外周。
一对第二弹性件320分别位于分隔部110沿活塞组件200的运动方向的两侧；进一步地，一对第二弹性件320的一端分别抵接于导向套112，另一端分别抵接于第一活塞220和第二活塞230；更进一步地，导向套112具有第一限位面1121和第二限位面1122，第一限位面1121和第二限位面1122沿塞杆210的轴向相背设置；一对所述第二弹性件320的一端分别抵接于所述第一限位面1121、所述第二限位面1122。作为一示例，第一弹性件310套设于第二弹性件320的外周。
在一实施方式中，第一段112a背向第二段112b的一端具有第一限位面1121，第二段112b背向第一段112a的一端具有第二限位面1122。
其中，活塞组件200封堵第一阀口102a和第二阀口102b其中一个时，第二弹性件320向活塞组件200提供的第二弹性力大于第一弹性件310向活塞组件200提供的第一弹性力。
作为一示例，活塞组件200封堵第一阀口102a和第二阀口102b其中一个时，一对第二弹性件320的长度分别为L3、L4，L3大于L4，第二弹性件320的自由长度为L”，L4<L”＜(L3+L4)/2，且L’≥L1。其中，L”可以小于L’。
需要说明的的是，如图15所示，曲线2(L2<L’≤(L1+L2)/2)中有弹性合力为零的行程(例如横坐标40％～60％)，在这个区间下容易出现因弹性合力为零而导致活塞组件200不稳定而上下晃动，从而产生噪音振动的问题。L’≥L1时，活塞组件200始终与一对第二弹性件320接触，一对第二弹性件320对活塞组件200进行支撑，活塞组件200整个过程中稳定运行，不会出现晃动。
此外，图15中同一横坐标下，曲线1对应的弹性合力大于曲线2对应的弹性合力，如此会导致活塞组件200在整个运动形成中均受到较大的弹性力，这不利于提升动作能力。
基于此，本公开实施例的切换阀设置一对第一弹性件310和一对第二弹性件320，第一弹性件310的自由长度设计为L’≥L1，第二弹性件320的自由长度设计为L4<L”＜(L3+L4)/2，一对第一弹性件310和一对第二弹性件320的弹性合力在活塞组件200的整个运动行程中分别形成了两条曲线，两条曲线耦合后形成了如图16所示的曲线。图16中活塞组件200在整个运动行程中受到的最大弹性合力与图4所示的活塞组件200在整个运动行程中受到的最大弹性力相等，并且，所述活塞组件封堵所述第一阀口和所述第二阀口其中一个时，所述第二弹性件向所述活塞组件提供的第二弹性力大于所述第一弹性件向所述活塞组件提供的第一弹性力，使得活塞组件200在较大第二弹性力的作用下向平衡状态所在的位置移动。即较大弹力的第二弹性件有效提升了阀的动作能力，较大的第二弹性件的弹力能够顺利开启第一阀口102a。
由图16可以看出，在横坐标10％～90％的区间内，仅一对第一弹性件310提供的弹性合力作用在活塞组件200上，且该弹性合力较小，在阀切换时需要克服的阻力变小，进而有效提升了阀的动作能力；此外，L’≥L1，一对第一弹性件可起到稳定活塞组件的作用，防止活塞组件200产生噪音振动。
由此可见，本公开实施例的切换阀，可兼顾提升阀的动作能力以及防止活塞组件200产生噪音振动的问题。
可以理解的是，本实施例的设计可应用与上述任一实施例的切换阀，此处不再一一列举。
【实施例七】
如图17和图18所示，本公开第七实施例与上述实施例的相同之处不再赘述，其不同之处在于：
本公开实施例的切换阀包括阀体100、活塞组件200和弹性件，弹性件包括一对第一弹性件310。阀体100具有内腔101，内腔101具有第一通道102和第二通道103；活塞组件200可动地设于内腔101内，用于封堵第一通道102和/或第二通道103；其中，第一通道102、第二通道103沿活塞组件200的运动方向布置。弹性件用于使活塞组件200处于平衡状态。活塞组件200处于平衡状态时，活塞组件200同时封堵第一通道102和第二通道103。
本公开实施例的切换阀，活塞组件200处于平衡状态时，第一通道102、第二通道103均处于关闭状态，此时流体通过切换阀时因节流施加给活塞组件200的流体驱动力最大，因此最大限度地提高了切换阀的动作能力，提升了切换阀动作的可靠性。例如可将活塞组件由第一通道102封堵、第二通道103打开的状态切换至第二通道103封堵、第一通道102打开。其中，第一通道102封堵、第二通道103打开的状态转换至第一通道102封堵、第二通道103封堵的过程中，驱动活塞组件200运动的力为弹性件与流体力。第一通道102封堵、第二通道103封堵的状态切换至第二通道103封堵、第一通道102打开，需要克服弹性件的弹力，而此时因第二通道103封堵而导致节流，因节流而产生的流体驱动力刚好可克服弹性件的弹力。在一实施方式中，弹性件包括一对第一弹性件310。为了便于说明，一对第一弹性件310分别定义为第一弹性部310a和第二弹性部310b。一对第一弹性件310可保证活塞组件200处于平衡状态的稳定性。此外，第一弹性部310a用于向活塞组件200提供朝着封堵第二通道103的位置移动的第一弹性力；第二弹性部310b用于向活塞组件200提供朝着封堵第一通道102的位置移动的第二弹性力。
如图18所示，内腔101内设有分隔部110，分隔部110将内腔101分隔为第一通道102和第二通道103；第一弹性部310a位于第一通道102内，第二弹性部310b位于第二通道103内。
活塞组件200包括塞杆210、第一活塞220和第二活塞230。第一活塞220连接于塞杆210的轴向一端，用于封堵第一通道102。第一弹性部310a的一端与分隔部110抵接，另一端与第一活塞220抵接；第二活塞230连接于塞杆210的轴向另一端，用于封堵第二通道103，第二弹性部310b的一端与分隔部110抵接，另一端与第二活塞230抵接。
于本公开实施例中，第一弹性部310a的一端抵接于分隔部110，另一端抵接于第一活塞220，第一弹性部310a提供的第一弹性力用于使第一活塞220具有打开第一通道102的趋势；第二弹性部310b的一端抵接于分隔部110，另一端抵接于第二活塞230，第二弹性部310b提供的第二弹性力用于使第二活塞230具有打开第二通道103的趋势。
在一实施方式中，第一弹性部310a、第二弹性部310b可以为压簧，且套设于塞杆210的外周。
第一活塞220包括第一本体221和第一密封圈222，第一本体221与塞杆210的轴向一端连接，第一密封圈222套设于第一本体221的外周，用于与第一通道102密封配合。其中，第一本体221与塞杆210可以通过螺接、过盈配合、焊接等方式连接。
第二活塞230包括第二本体231和第二密封圈232，第二本体231与塞杆210的轴向另一端连接，第二密封圈232套设于第二本体231的外周，用于与第二通道103密封配合。其中，第二本体231与塞杆210可以通过螺接、过盈配合、焊接等方式连接。
分隔部110包括分隔环111和导向套112，分隔环111固定连接于内腔101的腔壁，且环绕连接于导向套112的外周，塞杆210可动地穿设于导向套112内。
于本公开实施例中，塞杆210与导向套112导向配合，提高了塞杆210运动的稳定性，进而提高了阀动作的可靠性。
如图18所示，导向套112的轴向两端具有第一限位面1121和第二限位面1122，第一限位面1121和第二限位面1122沿活塞组件200的运动方向相背设置。第一限位面1121被配置为当活塞组件200封堵第一通道102且移动至第一极限位置时抵接活塞组件200的第一活塞220，第二限位面1122被配置为当活塞组件200封堵第二通道103且移动至第二极限位置时抵接活塞组件200的第二活塞230。换言之，活塞组件200位于第一极限位置时，第一限位面1121与第一活塞220抵接，且第二通道103处于最大打开状态；活塞组件200位于第二极限位置时，第二限位面1122与第二活塞230抵接，且第一通道102处于最大打开状态。
于本公开实施例中，通过设置第一限位面1121和第二限位面1122，可对活塞组件200位于第一极限位置和第二极限位置时进行限位。
如图18所示，分隔环111具有第一环面1111和第二环面1112，第一环面1111和第二环面1112沿活塞组件200的运动方向相背设置；导向套112伸出于第一环面1111的部分定义为第一段112a，第一弹性部310a套设于第一段112a的外周；导向套112伸出于第二环面1112的部分定义为第二段112b，第二弹性部310b套设于第二段112b的外周。
【实施例八】
本公开第八实施例与上述实施例的相同之处不再赘述，其不同之处在于：
如图19和图20所示，本公开实施例的切换阀包括阀体10c与活塞组件20c。阀体10c包括内腔11c，内腔11c具有第一阀口101c与第二阀口102c；活塞组件20c在内腔11c内可移动地设置，活塞组件20c包括塞杆21c、第一活塞22c和第二活塞23c，第一活塞22c和第二活塞23c分别连接于塞杆21c的相对两端，第一阀口101c与第二阀口102c沿活塞组件20c的运动方向上间隔布置，第一活塞22c用于封堵第一阀口101c，第二活塞23c用于封堵第二阀口102c；其中，第一活塞22c和第二活塞23c中至少之一注塑成型。
本公开的切换阀，注塑成型的第一活塞22c和/或第二活塞23c有利于控制切换阀的重量以及成本。此外，活塞组件20c在内腔11c内移动的过程中，注塑成型的第一活塞22c和/或第二活塞23c可以降低与内腔11c内壁以及第一阀口101c与第二阀口102c摩擦、撞击的异响，从而提高切换阀的静音效果。
具体地，参考图19至图23所示，阀体10c可以包括阀座12c与阀盖13c，阀座12c具有内腔11c，阀盖13c连接于阀座12c。其中，阀盖13c由金属材料制成，阀座12c可以由金属材料或塑料材质制成，塑料材质的阀座12c轻便且有利于节省成本。
在一种实施方式中，阀盖13c具有贯通的第一开口131c，以使第一开口131c与内腔11c相连通，阀座12c具有贯通的第二开口121c，以使第二开口121c与内腔11c相连通。其中，第一活塞22c封堵第一阀口101c时，第一开口131c与第二开口121c不连通；第二活塞23c封堵第二阀口102c时，第一开口131c与第二开口121c连通。在一些实施方式当中，第一开口131c可作为切换阀的流体进口，可以与压缩机的出口连通。第二开口121c可作为切换阀的流体出口，可以与压缩机的进口连通。阀座12c远离阀盖13c的一端可作为切换阀流体的另一进口，可与压缩机的进口连通，第一活塞22c封堵第一阀口101c时，第二开口121c与该流体进口连通。即，本公开的切换阀可为三通阀，包括两处流体进口与一处流体出口。
在另一种实施方式中，阀座12c具有贯通的第一开口131c，以使第一开口131c与内腔11c相连通，阀座12c具有贯通的第二开口121c，以使第二开口121c与内腔11c相连通。即，第一开口131c与第二开口121c均设于阀座12c。第一活塞22c封堵第一阀口101c时，第一开口131c与第二开口121c不连通；第二活塞23c封堵第二阀口102c时，第一开口131c与第二开口121c连通。
在本公开的一种示例性实施方式中，参考图19、图20所示，阀座12c具有第三开口122c，第三开口122c沿阀座12c的径向设置且与内腔11c相连通；部分阀盖13c伸入至第三开口122c内，或阀盖13c套设于第三开口122c外。为便于阀盖13c与阀座12c连接，阀座12c具有第三开口122c的一端设有铆接部，铆接部与阀盖13c相连。或者，阀盖13c靠近阀座12c的一端设有铆接部，铆接部与阀座12c相连。
在本公开的一种示例性实施方式中，参考图20所示，阀盖13c具有伸入第三开口122c内的贴合段132c，贴合段132c的外周面与第三开口122c的内周面过盈配合。例如，贴合段132c在阀盖13c未与阀座12c配合前的外径，大于贴合段132c在阀盖13c与阀座12c配合后的外径。或参考图21所示，阀盖13c具有套设在第三开口122c外的贴合段132c，贴合段132c的内周面与第三开口122c的所在阀座位置的外周面过盈配合。
在本公开的一种示例性实施方式中，阀盖13c与阀座12c还可以采用螺纹连接的方式连接，或焊接固定为一体，或者，在一些示例性实施方式中，阀盖13c与阀座12c还可以一体成型设置。
在本公开的一种示例性实施方式中，参考图19至图22所示，弹性件包括第一弹性部31c与第二弹性部32c，内腔11c设有将第一阀口101c与第二阀口102c分割开的分隔部125c；第一弹性部31c套设于塞杆21c，且位于第一活塞22c与分隔部125c之间，第一弹性部31c的相对两端分别与第一活塞22c和分隔部125c相抵接；第二弹性部32c套设于塞杆21c，且位于第二活塞23c与分隔部125c之间，第二弹性部32c的相对两端分别与第二活塞23c和分隔部125c相抵接。
第一弹性部31c与第二弹性部32c用于保持活塞组件20c在平衡状态时的稳定性。本公开所述平衡状态，是指在无流体冲击下，活塞组件20c相对于阀体10c保持不动的状态。第一弹性部31c用于向活塞组件20c施加使第二活塞23c向封堵第二阀口102c的位置移动的弹性力，第二弹性部32c用于向活塞组件20c施加使第一活塞22c向封堵第一阀口101c的位置移动的弹性力。在一种示例性实施方式中，当活塞组件20c处于平衡状态时，第一弹性部31c与第二弹性部32c作用于活塞组件20c的弹力与活塞组件20c的重力的合力为零。
在本公开的一种示例性实施方式中，第一弹性部31c可以为压簧，第二弹性部32c可以为压簧。
请参考图19至图21所示，在本公开的一种示例性实施方式中，阀座12c包括同轴设置且相连的第一阀套123c与第二阀套124c。其中，阀盖13c与第一阀套123c连接，第二阀套124c与第一阀套123c连接，第二阀套124c的两端分别形成第一阀口101c与第二阀口102c。第一阀套123c与第二阀套124c可以一体成型。示例性地，第一开口131c可以设于第一阀套123c的周侧壁，第二开口121c设置于第二阀套124c。在另一些实施例中，阀座12c也可以不包括第一阀套123c而具有第二阀套124c，第一开口131c可以设于阀盖13c。
在本公开的一种示例性实施方式中，阀座12c还可以包括第三阀套，第三阀套与第二阀套124c同轴设置且连接于第二阀套124c远离第一阀套123c的一侧。第一阀套123c、第二阀套124c以及第三阀套可以一体成型。阀座12c远离阀盖13c的一端的流体进口可设置在第三阀套的周侧壁。
在本公开的一种示例性实施方式中，参考图20所示，第二阀套124c的外径的最大值小于第一阀套123c的外径的最大值。示例性地，还可以是第二阀套124c的外径的最大值小于第一阀套123c的外径的最大值，且第三阀套的外径的最大值小于第一阀套123c的外径的最大值。
在本公开的一种示例性实施方式中，参考图19所示，第一活塞22c包括第一本体221c以及套设于第一本体221c外周的第一密封圈222c。第一活塞22c封堵第一阀口101c时，第一密封圈222c压缩于第一本体221c与第一阀口101c之间，以密封第一阀口101c。第二活塞23c包括第二本体231c以及套设于第二本体231c外周的第二密封圈232c，第二活塞23c封堵第二阀口102c时，第二密封圈232c用于压缩于第二本体231c与第二阀口102c内壁之间，以密封第二阀口102c。第一密封圈222c、第二密封圈232c可以为弹性材质，例如橡胶制成。第一本体221c与塞杆21c可以通过螺接、过盈配合、焊接、注塑等方式连接；第二本体231c与塞杆21c可以通过螺接、过盈配合、焊接、注塑等方式连接。
本领域技术人员应当理解的是，本公开所述“第一活塞22c和第二活塞23c中至少之一注塑成型”，指的是第一本体221c与第二本体231c中至少之一注塑成型，而并不意味着第一密封圈222c也与第一本体221c注塑成型，或第二密封圈232c也与第二本体231c注塑成型。
参考图20、图21所示，阀体10c具有第一端面1241c，优选第二阀套124c具有第一端面1241c，第一端面1241c位于第一阀口101c靠近阀盖13c的一端，第一活塞22c具有第一限位面223c，用于在第一活塞22c封堵第一阀口101c时，与第一端面1241c相抵接。当第一限位面223c与第一端面1241c相抵时，第一活塞22c向第一阀口101c方向运动至极限位置，第一本体221c以及压缩的第一密封圈222c将第一阀口101c密封封堵。示例性地，阀体10c具有第二端面1242c，优选第二阀套124c具有第二端面1242c，第二端面1242c位于第二阀口102c远离阀盖13c的一端，第二活塞23c具有第二限位面233c，用于在第二活塞23c封堵第二阀口102c时，与第二端面1242c相抵接。当第二限位面233c与第二端面1242c相抵时，第二活塞23c向第二阀口102c方向运动至极限位置，第二本体231c以及压缩的第二密封圈232c将第二阀口102c密封封堵。
在本公开的一种示例性实施方式中，塞杆21c可以包括金属材料，例如，塞杆21c不包括非金属材料。第一活塞22c可以为塑料材质。第一活塞22c可以以塞杆21c为金属嵌件，一体注塑形成第一活塞22c。第二活塞23c可以包括金属材料，通过机械加工的方式形成，并可与塞杆21c机械连接。第二活塞23c还可以与塞杆21c为同种金属材料。或第二活塞23c可以为塑料材质。
又例如，塞杆21c为塑料材质，第一活塞22c可以为塑料材质，塞杆21c可以与第一活塞22c一体注塑成型。第二活塞23c可以包括金属材料，通过机械加工的方式形成，并可与塞杆21c机械连接。又例如，第一活塞22c、第二活塞23c均可以为塑料材质。
阀盖13c可以由金属材料制成，例如包括铝合金。例如，阀盖13c为铝合金材料制成。在本公开的一种示例性实施方式中，可以是铝合金材料的阀盖13c与注塑成型的阀座12c相配合，也可以是铝合金材料的阀盖13c与金属材料制成的阀座12c相配合。
例如，在一种实施例中，阀盖13c、阀座12c、塞杆21c均可以为铝合金材料制成。阀盖13c与阀座12c可以采用螺纹连接、焊接、过盈配合等方式连接。塞杆21c、第一本体221c与第二本体231c可以分别加工成型后，通过螺接、过盈配合、焊接、注塑等方式连接。或者，第一本体221c与塞杆21c一体成型，第二本体231c与塞杆21c机械连接；或，第二本体231c与塞杆21c一体成型，第一本体221c与塞杆21c机械连接；或第一本体221c和第二本体231c均与塞杆21c一体成型。参考图21所示，第一开口131c设于阀盖13c，从而可以使阀座12c的长度相对缩短，便于阀座12c的金属机械加工。
例如，在一种实施例中，阀盖13c、塞杆21c均可以为铝合金材料制成。阀座12c为塑料材质注塑成型，阀盖13c与阀座12c可以铆接，或者采用过盈配合的方式连接。塞杆21c、第一本体221c与第二本体231c的成型及连接方式可以参考前述实施例。参考图20所示，第一开口131c可以设于阀座12c，具体地可以设于第一阀套123c，从而使阀盖13c的长度可以相对缩短，便于阀盖13c的金属机械加工。
又例如，在一种实施例中，阀盖13c为金属材料制成，例如可以为铝合金材料制成。阀座12c为塑料材质注塑成型，阀盖13c与阀座12c可以铆接，或者采用过盈配合的方式连接。塞杆21c为金属材料制成，例如可以为铝合金材料制成。第一活塞22c可以为塑料材质，第一活塞22c以塞杆21c为嵌件，一体注塑成型。第二活塞23c包括金属材料，通过机械加工的方式形成，并可与塞杆21c机械连接。或，第二活塞23c可以为塑料材质，第二活塞23c以塞杆21c为嵌件，一体注塑成型，第一活塞22c包括金属材料，通过机械加工的方式形成，并可与塞杆21c机械连接。参考图20所示，第一开口131c可以设于阀座12c，具体地可以设于第一阀套123c，从而使阀盖13c的长度可以相对缩短，便于阀盖13c的金属机械加工。
在本公开的一种示例性实施方式中，活塞组件20c与阀口之间形成节流通道，其中，活塞组件20c处于平衡状态时，节流通道的最大流通面积与阀口的最大流通面积的比值≤3/10。节流通道使活塞组件20c从处于平衡状态至阀口完全关闭范围内，流体一直可对活塞组件20c产生较大的驱动力，有利于提高切换阀的动作能力。
具体地，本公开所述阀口的最大流通面积，是指阀口完全打开时的流体流通截面积，即阀口的开口面积。节流通道的流通面积是指节流通道的开口面积。
例如，节流通道包括第一节流通道111c，第一活塞22c的外周面与第一阀口101c之间形成第一节流通道111c，第一节流通道111c的最大流通面积与第一阀口101c最大流通面积的比值≤3/10。例如，节流通道还可以包括第二节流通道112c，第二活塞23c的外周面与第二阀口102c之间形成第二节流通道112c，第二节流通道112c的最大流通面积与第二阀口102c最大流通面积的比值≤3/10。第一节流通道111c与第二节流通道112c可以提高切换阀工作时的动作能力，降低动作压差。
请参考图20至图21所示，示例性地，第一阀口101c具有内圆锥面，内圆锥面向第二阀套124c的方向收缩。第一密封圈222c压缩于第一本体221c与第一阀口101c之间，以密封第一阀口101c时，内圆锥面可以构成第一节流通道111c的内壁，在第一活塞22c封堵第一阀口101c的过程中，第一节流通道111c的流通面积逐渐变小，节流产生的流体力随着第一活塞22c逐渐封堵第一阀口101c而逐渐增大，第一弹性部31c的弹力逐渐增大，这样可克服随着第一阀口101c关闭而逐渐增大的弹性力，以进一步提高阀动作能力。此外，内圆锥面向第二阀套124c的方向收缩，还能避免因第一节流通道111c过窄，第一密封圈222c过度压缩，导致活塞组件20c卡死。
示例性地，第二阀口102c也具有内圆锥面，且内圆锥面向第二阀套124c的方向收缩。第二密封圈232c压缩于第二本体231c与第二阀口102c内壁之间，以密封第二阀口102c时，内圆锥面可以构成第二节流通道112c，在第二活塞23c封堵第二阀口102c的过程中，第二节流通道112c的流通面积逐渐变小，节流产生的流体力随着第二活塞23c逐渐封堵第二阀口102c而逐渐增大，第二弹性部32c的弹力逐渐增大，这样可克服随着第二阀口102c关闭而逐渐增大的弹性力，以进一步提高阀动作能力。此外，内圆锥面向第二阀套124c的方向收缩，还能避免因第二节流通道112c过窄，第二密封圈232c过度压缩，导致活塞组件20c卡死。
请参考图20至图21所示，阀盖13c设有导向孔133c，塞杆21c与第一活塞22c相连的一端穿过第一活塞22c，伸入至导向孔133c内，塞杆21c在导向孔133c内可移动地设置，以对活塞组件20c的往复移动起到导向作用，并可以支撑塞杆21c，增加塞杆21c的支撑刚度。
在本公开的一种示例性实施方式中，阀体10c作为插装阀安装至安装座(图中无示意)内。阀体10c外设有限位台，阀体10c外周设有螺纹连接部，螺纹连接部与安装座螺纹连接。当螺纹连接部与安装座螺纹连接后，限位台与安装座抵接。限位台与螺纹连接部共同实现阀体10c的限位，限位台防止阀体10c往下侧运动，螺纹连接部可以防止阀体往上侧运动。
本公开的另一方面，还提供一种制冷系统，包括上述任一项的切换阀。由于包括上述任一实施例的切换阀，故本公开实施例的制冷系统包括上述任一实施例的所有优点和有益效果，此处不再赘述。
可以理解的是，本公开提供的各个实施例/实施方式在不产生矛盾的情况下可以相互组合，此处不再一一举例说明。
在申请实施例中，术语“第一”、“第二”、“第三”仅用于描述的目的，而不能理解为指示或暗示相对重要性；术语“多个”则指两个或两个以上，除非另有明确的限定。术语“安装”、“相连”、“连接”、“固定”等术语均应做广义理解，例如，“连接”可以是固定连接，也可以是可拆卸连接，或一体地连接；“相连”可以是直接相连，也可以通过中间媒介间接相连。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在申请实施例中的具体含义。
申请实施例的描述中，需要理解的是，术语“上”、“下”、“左”、“右”、“前”、“后”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述申请实施例和简化描述，而不是指示或暗示所指的装置或单元必须具有特定的方向、以特定的方位构造和操作，因此，不能理解为对申请实施例的限制。
在本说明书的描述中，术语“一个实施例”、“一些实施例”、“具体实施例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或特点包含于申请实施例的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或实例。而且，描述的具体特征、结构、材料或特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
以上仅为申请实施例的优选实施例而已，并不用于限制申请实施例，对于本领域的技术人员来说，申请实施例可以有各种更改和变化。凡在申请实施例的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在申请实施例的保护范围之内。

Claims (34)

  1. 一种切换阀，其中，包括：
    阀体，包括具有阀口的内腔；
    活塞组件，可动地设于所述内腔内，用于封堵或打开所述阀口；
    弹性件，用于使所述活塞组件处于平衡状态；所述平衡状态是指：在无流体冲击下，所述活塞组件相对于所述阀体保持不动；
    所述活塞组件与所述内腔的腔壁之间形成与所述阀口连通的节流通道；其中，所述活塞组件处于所述平衡状态时，所述节流通道的最大流通面积与所述阀口最大流通面积的比值≤3/10。
  2. 根据权利要求1所述的切换阀，其中，所述活塞组件处于所述平衡状态时，所述阀口的内周面与所述活塞组件之间形成所述节流通道。
  3. 根据权利要求2所述的切换阀，其中，所述活塞组件具有用于与所述阀口密封配合的第二外圆锥面。
  4. 根据权利要求2所述的切换阀，其中，所述活塞组件包括用于伸入所述阀口内的第一活塞片；
    所述活塞组件还包括第二活塞片和第三活塞片，所述第二活塞片夹设于所述第一活塞片和所述第三活塞片之间，所述第二活塞片具有与所述阀口密封配合的第二外圆锥面。
  5. 根据权利要求1所述的切换阀，其中，所述阀体包括同轴设置的第一阀套和第二阀套，所述第二阀套具有所述阀口；
    所述第一阀套的内周面与所述活塞组件之间和/或所述第二阀套的内周面与所述活塞组件之间形成所述节流通道。
  6. 根据权利要求5所述的切换阀，其中，所述活塞组件在封堵所述阀口的过程中，所述第一阀套的内周面与所述活塞组件之间形成的所述节流通道的流通面积逐渐变小。
  7. 根据权利要求6所述的切换阀，其中，所述第一阀套的内周面具有内圆锥面或所述活塞组件的外周面具有第一外圆锥面。
  8. 根据权利要求1所述的切换阀，其中，所述阀口包括第一阀口和第二阀口，所述活塞组件的一端与所述第一阀口密封配合，另一端与所述第二阀口密封配合；所述第一阀口的最大流通面积为S11，所述第二阀口的最大流通面积为S12；
    所述活塞组件处于所述平衡状态时，所述节流通道包括与所述第一阀口连通的第一节流通道以及与所述第二阀口连通的第二节流通道，所述第一节流通道的最大流通面积为S21，所述第二节流通道的最大流通面积为S22；S21/S11≤3/10，S22/S12≤3/10。
  9. 根据权利要求8所述的切换阀，其中，所述第一节流通道位于所述第一阀口外，流体经所述第一节流通道流至所述第一阀口；所述第二节流通道位于所述第二阀口外，流体经所述第二节流通道流至所述第二阀口。
  10. 根据权利要求8或9所述的切换阀，其中，
    所述活塞组件处于所述平衡状态时，所述节流通道还包括与所述第一阀口连通的第三节流通道以及与所述第二阀口连通的第四节流通道，所述第三节流通道的最大流通面积为S31，所述第四节流通道的最大流通面积为S32，部分所述活塞组件伸入所述第一阀口内，且与所述第一阀口的孔壁之间形成所述第三节流通道，部分所述活塞组件伸入所述第二阀口内，且与所述第二阀口的孔壁之间形成所述第四节流通道，并且，S31/S11≤3/10，S32/S12≤3/10。
  11. 根据权利要求1所述的切换阀，其中，所述弹性件包括第一弹性部和第二弹性部，所述阀口包括第一阀口和第二阀口；
    所述内腔内设有分隔部，所述分隔部将所述第一阀口和所述第二阀口隔开；
    所述第一弹性部和所述第二弹性部分别位于所述分隔部沿所述活塞组件的运动方向的两侧，所述第一弹性部的一端与所述分隔部抵接，另一端与所述活塞组件的一端抵接；所述第二弹性部的一端与所述分隔部抵接，另一端与所述活塞组件的另一端抵接。
  12. 根据权利要求11所述的切换阀，其中，所述分隔部包括分隔环和导向套，所述分隔环固定连接于所述内腔的腔壁，且环绕连接于所述导向套的外周，所述活塞组件可动地穿设于所述导向套内。
  13. 根据权利要求1所述的切换阀，其中，所述活塞组件包括塞杆和活塞，所述活塞连接于所述塞杆，用于封堵所述阀口；
    所述阀体包括相连接的阀盖与阀座，阀座具有内腔，阀盖具有导向部，所述塞杆与所述导向部导向配合。
  14. 根据权利要求13所述的切换阀，其中，所述活塞包括沿所述塞杆的轴向间隔布置的第一活塞和第二活塞，所述阀口包括第一阀口和第二阀口，所述第一活塞用于封堵或打开所述第一阀口，所述第二活塞用于封堵或打开所述第二阀口；
    所述塞杆具有导向段，所述导向段位于所述第一活塞背向所述第二活塞的一侧，所述导向段与所述导向部导向配合。
  15. 根据权利要求1所述的切换阀，其中，所述内腔具有第一通道和第二通道；所述活塞组件用于封堵所述第一通道和/或所述第二通道；
    其中，所述活塞组件处于所述平衡状态时，所述活塞组件同时封堵所述第一通道和所述第二通道。
  16. 根据权利要求15所述的切换阀，其中，所述内腔内设有分隔部，所述分隔部将所述内腔分隔为所述第一通道和所述第二通道；
    所述弹性件包括第一弹性部与第二弹性部；
    所述第一弹性部位于所述第一通道内，且所述第一弹性部的一端与所述分隔部抵接，另一端与所述活塞组件的一端抵接；所述第二弹性部位于所述第二通道内，且所述第二弹性部的一端与所述分隔部抵接，另一端与所述活塞组件的另一端抵接；所述第一弹性部与所述第二弹性部用于使所述活塞组件处于平衡状态。
  17. 根据权利要求16所述的切换阀，其中，所述分隔部具有导向孔，所述导向孔沿所述活塞组件的运动方向贯穿所述分隔部；所述活塞组件可动地穿设于所述导向孔。
  18. 根据权利要求17所述的切换阀，其中，所述分隔部包括分隔环和导向套，所述分隔环固定连接于所述内腔的腔壁，且环绕连接于所述导向套的外周，所述导向套具有所述导向孔。
  19. 根据权利要求18所述的切换阀，其中，所述导向套的轴向两端具有第一限位面和第二限位面，所述第一限位面和所述第二限位面沿所述活塞组件的运动方向相背设置；
    所述第一限位面被配置为当所述活塞组件封堵所述第一通道且移动至第一极限位置时抵接所述活塞组件，所述第二限位面被配置为当所述活塞组件封堵所述第二通道且移动至第二极限位置时抵接所述活塞组件。
  20. 根据权利要求18所述的切换阀，其中，所述分隔环具有第一环面和第二环面，所述第一环面和所述第二环面沿所述活塞组件的运动方向相背设置；
    所述导向套伸出于所述第一环面的部分定义为第一段，所述第一弹性部套设于所述第一段的外周；所述导向套伸出于所述第二环面的部分定义为第二段，所述第二弹性部套设于所述第二段的外周。
  21. 根据权利要求16所述的切换阀，其中，所述活塞组件包括：
    塞杆，可动地穿设于所述分隔部；
    第一活塞，连接于所述塞杆的轴向一端，用于封堵所述第一通道，所述第一弹性部的另一端与所述第一活塞抵接；以及
    第二活塞，连接于所述塞杆的轴向另一端，用于封堵所述第二通道，所述第二弹性部的另一端与所述第二活塞抵接。
  22. 根据权利要求21所述的切换阀，其中，所述第一弹性部、所述第二弹性部套设于所述塞杆的外周。
  23. 根据权利要求21所述的切换阀，其中，所述第一活塞包括第一本体和第一密封圈，所述第一本体与所述塞杆的轴向一端连接，所述第一密封圈套设于所述第一本体的外周，用于与所述第一通道密封配合；
    所述第二活塞包括第二本体和第二密封圈，所述第二本体与所述塞杆的轴向另一端连接，所述第二密封圈套设于所述第二本体的外周，用于与所述第二通道密封配合。
  24. 根据权利要求1所述的切换阀，其中，所述阀口包括第一阀口与第二阀口；
    所述活塞组件包括塞杆、第一活塞和第二活塞，所述第一活塞和所述第二活塞分别连接于所述塞杆的相对两端，所述第一阀口与所述第二阀口沿所述活塞组件的运动方向上间隔布置，所述第一活塞用于封堵所述第一阀口，所述第二活塞用于封堵所述第二阀口；
    其中，所述第一活塞和第二活塞中至少之一注塑成型。
  25. 根据权利要求24所述的切换阀，其中，所述塞杆包括金属材料，所述第一活塞包括塑料材料；所述第一活塞以所述塞杆为金属嵌件，一体注塑成型；或，所述塞杆包括塑料材料，所述第一活塞包括塑料材料，所述塞杆与所述第一活塞一体注塑成型。
  26. 根据权利要求25所述的切换阀，其中，当所述塞杆包括金属材料时，所述塞杆与包括金属材料的所述第二活塞固定连接；或，所述塞杆与包括塑料材料的所述第二活塞固定连接；
    当所述塞杆包括塑料材料时，所述塞杆与包括金属材料的所述第二活塞固定连接；或，所述塞杆与包括塑料材料的所述第二活塞固定连接。
  27. 根据权利要求24所述的切换阀，其中，当所述塞杆包括金属材料时，所述第一活塞包括金属材料，所述第二活塞包括塑料材料，所述第一活塞和所述塞杆固定连接，所述第二活塞以所述塞杆为金属嵌件，一体注塑成型；或当所述塞杆包括塑料材质时，所述第一活塞包括金属材料，所述第二活塞包括塑料材料，所述第一活塞和所述塞杆固定连接，所述第二活塞与所述塞杆一体注塑成型。
  28. 根据权利要求24所述的切换阀，其中，所述阀体包括阀座与阀盖，所述阀座具有所述内腔，所述阀盖连接于所述阀座；
    其中，所述阀盖由金属材料制成，所述阀座由金属材料或塑料材料制成。
  29. 根据权利要求28所述的切换阀，其中，所述阀座具有第三开口，所述第三开口沿所述阀座的径向设置且与所述内腔相连通；
    所述阀盖部分伸入至所述第三开口内或部分所述阀盖套设在所述第三开口外；
    所述阀座具有所述第三开口的一端设有铆接部，所述铆接部与所述阀盖相连；或所述阀盖靠近所述阀座的一端设有铆接部，所述铆接部与所述阀座相连。
  30. 根据权利要求28所述的切换阀，其中，所述阀座具有第三开口，所述第三开口沿所述阀座的径向设置且与所述内腔相连通；
    所述阀盖具有伸入所述第三开口内的贴合段，所述贴合段的外周面与所述第三开口的内周面过盈配合；或所述阀盖具有套设在所述第三开口外的贴合段，所述贴合段的内周面与所述第三开口的外周面过盈配合。
  31. 根据权利要求24所述的切换阀，其中，所述弹性件包括第一弹性部与第二弹性部，所述内腔设有将所述第一阀口与所述第二阀口分割开的分隔部；所述第一弹性部套设于所述塞杆，且位于所述第一活塞与所述分隔部之间，所述第一弹性部的相对两端分别与所述第一活塞和所述分隔部相抵接；所述第二弹性部套设于所述塞杆，且位于所述第二活塞与所述分隔部之间，所述第二弹性部的相对两端分别与所述第二活塞和所述分隔部相抵接；
    所述活塞组件处于平衡状态时，所述第一弹性部与所述第二弹性部作用于所述活塞组件的弹力与所述活塞组件的重力的合力为零。
  32. 根据权利要求24所述的切换阀，其中，所述第一活塞包括第一本体以及套设于所述第一本体外周的第一密封圈，所述第一活塞封堵所述第一阀口时，所述第一密封圈压缩于所述第一本体与所述第一阀口之间，以密封所述第一阀口；所述阀体具有第一端面，所述第一端面位于所述第一阀口远离所述第二阀口的一端，所述第一活塞具有第一限位面，用于在所述第一活塞封堵所述第一阀口时，与所述第一端面相抵接；和/或；
    所述第二活塞包括第二本体以及套设于所述第二本体外周的第二密封圈，所述第二活塞封堵所述第二阀口时，所述第二密封圈压缩于所述第二本体与所述第二阀口之间，以密封所述第二阀口；所述阀体具有第二端面，所述第二端面位于所述第二阀口远离所述第一阀口的一端，所述第二活塞具有第二限位面，用于在所述第二活塞封堵所述第二阀口时，与所述第二端面相抵接。
  33. 根据权利要求28或29所述的切换阀，其中，所述阀盖设有导向孔，所述塞杆与所述第一活塞相连的一端穿过所述第一活塞，伸入至所述导向孔内，所述塞杆在所述导向孔内可移动地设置。
  34. 根据权利要求24所述的切换阀，其中，所述切换阀还包括安装座；所述阀体外设有限位台并设有螺纹连接部；所述螺纹连接部与所述安装座螺纹连接后，所述限位台与所述安装座抵接。
PCT/CN2025/111781 2024-07-31 2025-07-31 切换阀 Pending WO2026026906A1 (zh)

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