CN107435754B

CN107435754B - Flow regulating valve

Info

Publication number: CN107435754B
Application number: CN201710296089.4A
Authority: CN
Inventors: 原田贵雄; 柳泽秀; 小泉佑树
Original assignee: Fujikoki Corp
Current assignee: Fujikoki Corp
Priority date: 2016-05-26
Filing date: 2017-04-28
Publication date: 2020-07-31
Anticipated expiration: 2037-04-28
Also published as: JP2017211032A; CN107435754A; JP6692215B2

Abstract

Provided is a flow rate control valve which can effectively reduce noise when a fluid (refrigerant) passes therethrough and can reduce pressure loss in a large-opening area. Silencing members (71, 72) for thinning bubbles in a fluid flowing through a small flow passage are disposed on the valve chamber (14) side and the valve port (16) side of a valve port (second valve port) (36) of the small flow passage for communicating the valve chamber (14) and the valve port (first valve port) (16) through a communication space (34), specifically, on a through port (33u) of an interlocking member (33) of a valve body (32) and a communication passage (37) of a valve body member (38).

Description

Flow regulating valve

Technical Field

The present invention relates to a flow rate adjustment valve suitable for adjusting a flow rate of a refrigerant in, for example, a heat pump type cooling and heating system, and more particularly to a flow rate adjustment valve capable of reducing noise when a fluid (refrigerant) passes therethrough.

Background

As an example of such a flow rate control valve, there is known an electrically operated valve including: a valve body provided with a valve chamber and a valve seat having a valve port (orifice); and a valve element that changes a flow rate of a fluid flowing through the valve port in accordance with an amount of lift from the valve seat, and is lifted and lowered so as to be brought into contact with, separated from, or brought close to, or separated from the valve seat by providing a screw-feed type lift driving mechanism including a valve shaft provided with a male screw, a bearing member provided with a female screw, a stepping motor, and the like as described in, for example, patent documents 1 and 2.

However, in the case of combining the flow rate adjustment valve of the structure described above to, for example, a heat pump type cooling and heating system, there are problems as follows: when the valve port is opened to a predetermined opening degree and the refrigerant flowing into the valve chamber flows out from the valve chamber through a gap formed between the valve element and the valve port, continuous noise (fluid passing sound) is likely to be generated.

More specifically, when a fluid (refrigerant) flowing into the valve port is in a mixed state of gas and liquid (gas-liquid two-phase flow), that is, when bubbles are mixed in the fluid flowing into the valve port through the valve chamber, rapid pressure fluctuations are generated on the inflow side and the outflow side of the fluid when the bubbles pass through the valve port, and large noise is generated due to the pressure fluctuations. In particular, in a small opening area (an area where the valve opening (the amount of lift of the valve element) is small), generally, the flow path of the fluid in the valve port (the gap between the valve element and the valve port) is very narrow, and therefore, the influence of bubbles in the fluid increases, and the above-described large noise (fluid passing sound) is more likely to occur.

To solve such a problem, in the conventional technique described in patent document 3, a member (muffler member) for thinning bubbles in a fluid is proposed to be disposed in a valve chamber

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2012-172839

Patent document 2: japanese patent laid-open publication No. 2004-289901

Patent document 3: japanese patent laid-open No. 2001 and 289538

Problems to be solved by the invention

However, in a large opening area (an area where the valve opening is large), a flow path of the fluid in the valve port (a gap between the valve body and the valve port) is enlarged, and thus it is difficult to generate such a large noise (fluid passage sound), and on the other hand, the necessity of sufficiently securing the flow rate passing through the valve port is increased.

In the conventional technique described in patent document 3, since the bubbles in the fluid flow into the gap between the valve element and the valve port in a state of being decomposed and thinned by the silencer, when passing through the valve port, rapid pressure fluctuations do not occur on the inflow side and the outflow side, and the noise can be reduced. However, since the muffler member is fixed to the valve body so as to always separate the inlet side and the outlet side of the valve chamber, there is a problem in that, in a large opening area where it is necessary to secure a flow rate passing through the valve port: the flow of fluid to the valve port is inhibited, the pressure loss (pressure loss) increases, and it is difficult to obtain an appropriate refrigerant flow rate.

Disclosure of Invention

The present invention has been made in view of the above circumstances, and an object thereof is to provide a flow rate control valve capable of effectively reducing noise when a fluid (refrigerant) passes therethrough and reducing pressure loss in a wide opening range.

Means for solving the problems

To achieve the above object, a flow rate control valve according to the present invention basically includes: a valve body provided with a valve chamber and a first valve port; a valve shaft disposed in the valve chamber so as to be vertically movable; an elevation drive unit for elevating the valve shaft; and a valve body that is slidably inserted into the valve shaft so as to surround an outer periphery of a lower end portion of the valve shaft and is driven in conjunction with an up-and-down movement of the valve shaft, wherein the valve body is provided with a first valve body portion that changes a flow rate of a fluid flowing through the first valve port in accordance with an amount of the rise, a small flow passage that communicates the valve chamber with the first valve port via a communication space defined by the valve body in the vicinity of the lower end portion of the valve shaft, and a second valve core portion that changes a flow rate of a fluid flowing through a second valve port provided in the small flow passage in accordance with an amount of the rise, and the valve shaft is provided with the second valve core portion that is configured to be in a small flow rate control state in which the first valve port is closed by the first valve body portion and the flow rate is controlled in accordance with an amount of the rise of the second valve core portion with respect to the second valve port when the amount of the rise of the second valve core portion is equal to or less than a, when the amount of lift of the second valve core portion exceeds the predetermined amount, a large flow rate control state is achieved in which the valve body is lifted in accordance with the lift of the valve shaft and the first valve body opens the first valve port, and a silencer member that thins bubbles in the fluid flowing through the small flow rate passage is disposed on the valve chamber side and the first valve port side of the second valve port of the small flow rate passage.

Preferably, the valve body is biased in a valve closing direction of the first valve port by a biasing member, and when an amount of lift of the second valve core portion exceeds the predetermined amount, the valve body is lifted by a flange-shaped locking portion provided on the valve shaft against a biasing force of the biasing member.

Preferably, the valve body is constituted by a cylindrical interlocking member slidably inserted externally on the upper side of the second valve core portion of the valve shaft, and a valve body member connected to a lower end opening of the interlocking member and provided with the first valve core portion.

In a preferred aspect, the small flow passage is constituted by a through-hole provided in the interlocking member to communicate the valve chamber with the communication space, the communication passage provided in the valve body member to communicate the communication space with the first port, the second port formed in the communication passage, and a communication passage provided in the interlocking member and the communication passage of the valve body member.

In a more preferred aspect, a cylindrical sound deadening member is disposed on an inner periphery of the interlocking member.

In a more preferred aspect, the cylindrical muffler member is disposed on the inner periphery of the interlocking member such that an upper end thereof is fitted into a recess provided in the interlocking member and a lower end thereof is sandwiched between the valve body member and the interlocking member.

In another preferred aspect, the muffler member supports the communication passage fixed to the valve body member by a support member having a through hole, and the support member is fixed to the communication passage of the valve body member.

In another preferred aspect, in a state where the first valve port is closed by the first valve core portion and the second valve port is closed by the second valve core portion, fluid is allowed to flow from the first valve port to the valve chamber, but a check spool is provided that prevents fluid from flowing from the valve chamber to the first valve port.

In a more preferred aspect, the valve shaft is provided with: a housing chamber housing the check valve body; a check valve port that communicates with the housing chamber and the first valve port and that is opened and closed by the check valve body according to a differential pressure between the first valve port side and the valve chamber side; and a communication port that is always communicated with the housing chamber and the valve chamber.

Effects of the invention

In the flow rate control valve of the present invention, since the silencing member for thinning bubbles in the fluid flowing through the small flow passage is disposed on the valve chamber side and the first valve port side of the second valve port of the small flow passage which communicates the valve chamber with the first valve port via the communication space, the noise when the fluid (refrigerant) passes can be effectively reduced, the pressure loss in the large opening degree (large flow rate control) region can be reduced, and an appropriate refrigerant flow rate can be obtained.

Drawings

Fig. 1 is an overall cross-sectional view showing an embodiment of a flow rate control valve according to the present invention.

Fig. 2 is a perspective view showing the interlocking member of the valve body shown in fig. 1 together with a sound deadening member.

Fig. 3 is a view showing a pressure plate of the valve body shown in fig. 1 together with a sound deadening member, where (a) is a perspective view and (B) is a bottom view.

Fig. 4 is a main sectional view showing a main portion (in the case of a forward flow) of the flow rate control valve shown in fig. 1, where (a) is a view showing a fully closed state, (B) is a view showing a state in which an amount of rise is small (a small flow rate control state), and (C) is a view showing a fully opened state (a large flow rate control state).

Fig. 5 is a main sectional view showing a main portion (in a reverse flow) of the flow rate control valve shown in fig. 1, where (a) is a view showing a fully closed state, (B) is a view showing a state where a check valve port is opened by a differential pressure, and (C) is a view showing a fully opened state.

Fig. 6 (a) to (C) are enlarged partial cross-sectional views each showing another example of the check valve structure shown in fig. 1.

Fig. 7 is an overall cross-sectional view showing a modification (one) of the flow rate control valve shown in fig. 1.

Fig. 8 is an overall sectional view showing a modification (two) of the flow rate control valve shown in fig. 1.

Description of the symbols

1 flow control valve

10 valve body

11 flow inlet

11A pipe joint

12 outflow opening

12A pipe joint

14 valve chamber

15 valve seat (first valve seat)

Valve port 16 (first valve port)

20 valve shaft

21 non-return valve core

21a compression coil spring

21b storage chamber

21u communication port

21v check valve port

22 screw drive member

27 screw feeding mechanism

28 thrust transmission shaft

29 connecting shaft

29a flange-like engaging portion

29b second valve core part (truncated cone)

30 outer cover

32 valve core

33 linkage part

33a cylindrical part of interlocking member

33b top of interlocking member

33c insertion part

33u through hole

34 communicating space

35 valve seat (second valve seat)

36 valve port (second valve port)

37 communication path

38 valve core part

38b first valve core (truncated cone)

39 compression coil spring (forcing part)

40 stator

50 rotor

60-singular planetary gear speed reducing mechanism

63 stepping motor (lifting driving part)

71 noise reduction component (valve chamber side noise reduction component)

72 silencing part (valve port side silencing part)

73 pressing plate (supporting parts)

73a through hole of the pressing plate

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

Fig. 1 is an overall cross-sectional view showing an embodiment of a flow rate control valve according to the present invention, fig. 2 is a perspective view showing an interlocking member of a valve body shown in fig. 1, fig. 3 is a view showing a pressure plate of the valve body shown in fig. 1, fig. 3 (a) is a perspective view, and fig. 3 (B) is a bottom view.

In the present specification, the description indicating the position and the direction such as up and down, left and right, front and back is added for convenience of the drawings to avoid the complexity of the description, and is not limited to the position and the direction in the actual use state.

In addition, the following may occur in each drawing: in order to facilitate understanding of the invention, for convenience of drawing, the gaps formed between the members, the spacing distance between the members, and the like are drawn to be larger or smaller than the size of each constituent member.

The flow rate adjustment valve 1 of the illustrated embodiment is an electrically operated valve used for adjusting the flow rate of refrigerant in, for example, a heat pump type cooling and heating system, and is configured by the following structure, as with the above-described conventional flow rate adjustment valve: a valve body 10, the valve body 10 having a valve chamber 14 into and from which a fluid (refrigerant) is introduced and discharged, and a valve seat (first valve seat) 15 having a valve port (first valve port) 16 opening into the valve chamber 14; a bottomed cylindrical case 30, the bottomed cylindrical case 30 being bonded to the valve main body 10 via an annular base plate 31; a stepping motor (lifting drive unit) 63, the stepping motor 63 being composed of a stator 40 fitted to the outer side of the housing 30 and a rotor 50 rotatably disposed on the inner periphery of the housing 30; a singular planetary gear reduction mechanism 60, the singular planetary gear reduction mechanism 60 reducing the rotational speed of the rotor 50; a valve shaft 20 provided with a valve body 32 that contacts and separates from the valve seat 15 to control the amount of fluid passing therethrough (in other words, changes the flow rate of the fluid flowing through the valve port 16 according to the amount of lift from the valve seat 15); and a screw feed mechanism 27 for converting the rotational motion of the output gear 57 of the singular planetary gear reduction mechanism 60 into a linear motion to drive the valve shaft 20 (to raise and lower the valve shaft 20) by the screw feed mechanism 27.

An inlet 11 to which a pipe joint 11A is connected is provided at one side portion of a valve chamber 14 of a valve body 10, an outlet 12 is provided at a bottom portion of the valve chamber 14 of the valve body 10, the pipe joint 12A is connected to the outlet 12, and a valve port (orifice) 16 composed of a valve seat 15 and a cylindrical surface is provided. A bearing member 13 is fitted into an upper portion of the valve chamber 14 of the valve body 10, the bearing member 13 is fixed to the valve body 10 by caulking (caulking portion 17), and a female screw portion 13a is formed in a lower half portion of a center portion of the bearing member 13. A lower end portion of the lid cylindrical housing 30 is hermetically joined to a base plate 31 fixed to (a stepped portion of) the outer periphery of the valve main body 10 by butt welding or the like.

The stator 40 attached to the outer periphery of the housing 30 is constituted by a yoke 41, a bobbin 42, a coil 43, a resin mold cover 44, and the like, and the rotor 50 rotatably supported (without moving up and down) inside the housing 30 is constituted by integrally coupling a cylindrical rotor member 51 made of a magnetic material and a sun gear member 52 made of a resin material. A shaft 62 is inserted into the center of the sun gear member 52, and the upper portion of the shaft 62 is supported by a support member 61 disposed inside the top portion of the housing 30.

The sun gear 53 of the sun gear member 52 meshes with a plurality of planetary gears 55, the plurality of planetary gears 55 are rotatably supported by a shaft 56, and the shaft 56 is provided on a carrier 54 placed on the bottom surface of an output gear 57. The upper half of the planetary gear 55 meshes with an annular ring gear (internal tooth fixed gear) 58, the lower half of the planetary gear 55 meshes with an internal gear 57a of an annular output gear 57, and the annular ring gear 58 is attached to the upper portion of the cylindrical member 18 fixed to the upper portion of the valve body 10 by caulking. The number of teeth of the ring gear 58 and the number of teeth of the ring gear 57a of the output gear 57 are slightly different, and thus the rotation speed of the sun gear 53 is reduced at a large reduction ratio and transmitted to the output gear 57 (such a gear structure is referred to as a so-called singular planetary gear reduction mechanism 60).

The output gear 57 is in sliding contact with the upper surface of the cylindrical bearing member 13, and the upper portion of a cylindrical output shaft 59 having a step is press-fitted into the center of the bottom portion of the output gear 57, and the lower portion of the output shaft 59 is rotatably inserted into a fitting hole 13b formed in the upper half portion of the center portion of the bearing member 13. A lower portion of the shaft 62 is fitted into an upper portion of the output shaft 59.

The valve shaft 20 includes, from the upper side, a screw drive member (also referred to as an actuator) 22, a stepped, shaft-shaped thrust transmission shaft 28, and a bottomed, cylindrical coupling shaft 29, the bottomed, cylindrical coupling shaft 29 being externally fitted and fixed to a lower portion of the thrust transmission shaft 28, and a valve body 32 being slidably externally fitted around the coupling shaft 29 so as to surround an outer periphery of a lower end portion of the coupling shaft 29 (i.e., an outer periphery of a lower end portion of the valve shaft 20).

A male screw portion 22a provided on (the outer periphery of) a screw drive member 22 constituting the valve shaft 20 is screwed into a female screw portion 13a provided on (the inner periphery of) the bearing member 13, and the screw drive member 22 converts the rotational motion of the output gear 57 (i.e., the rotor 50) into a linear motion in the axis O direction (the ascending/descending direction) by a screw feed mechanism 27 constituted by the male screw portion 22a and the female screw portion 13 a. Here, the output gear 57 is rotationally moved without moving up and down at a constant position in the axis O direction, the output shaft 59 is connected to the output gear 57, the flat-head-shaped plate portion 22b provided at the upper end portion of the screw drive member 22 is inserted into the slit-shaped fitting groove 59b provided at the lower end portion of the output shaft 59, and the rotational movement of the output gear 57 is transmitted to the screw drive member 22 side. The plate-like portion 22b provided in the screw driving member 22 slides in the axis O direction in the fitting groove 59b of the output shaft 59, so that when the output gear 57 (rotor 50) rotates, the screw driving member 22 is linearly moved in the axis O direction by the screw feeding mechanism 27 although the output gear 57 does not move in the rotation axis direction. The linear motion of the screw drive member 22 is transmitted to the thrust transmission shaft 28 via a ball joint 25 including balls 23 and a ball receiver 24, and the ball receiver 24 is fitted into a stepped fitting hole provided in an upper portion of the thrust transmission shaft 28. A coupling shaft 29 coupled to the thrust transmission shaft 28 is slidably inserted into (a lower portion of) a stepped cylindrical spring housing 19 fixed inside the valve main body 10, and the valve shaft 20 is guided by the spring housing 19 to move in the axis O direction. A compression coil spring 26 that constantly biases the valve shaft 20 in the valve opening direction (upward) is mounted in compression between (the upward stepped surface of) the spring housing 19 and (the downward stepped surface of) the thrust transmission shaft 28.

A flange-shaped engaging portion 29a that engages with (near the insertion portion 33c of) a top portion 33b of an interlocking member 33 (described later) is provided so as to protrude outward from the outer periphery of the lower end of (the cylindrical portion of) the connecting shaft 29, a communication port 21u formed of a plurality of lateral holes is provided below the flange-shaped engaging portion 29a, and a check valve port 21v formed of a vertical hole is provided in the center of the bottom portion of the connecting shaft 29. The coupling shaft 29 is provided with a housing chamber 21b formed of a cylindrical hollow cavity inside, and a check valve body 21 formed of a ball is slidably housed in the housing chamber 21b in the axis O direction in order to open and close a check valve port 21v (described later in detail) in accordance with a differential pressure between the inflow port 11 and the outflow port 12. A compression coil spring (urging member) 21a is compression-mounted between the check valve body 21 and the thrust transmission shaft 8, and an upper end of the compression coil spring 21a is externally fitted to a projecting portion 28a provided on a lower surface of the thrust transmission shaft 28 and constantly urges the check valve body 21 in a valve closing direction (downward). The lower end surface of the connecting shaft 29 is an inverted truncated cone-shaped second valve core portion 29b (truncated cone surface portion), and the inverted truncated cone-shaped second valve core portion 29b is in contact with and separated from a valve seat 35 provided in a valve body 32 described later to open and close the valve port 36.

The valve body 32 is constituted by a cylindrical interlocking member 33 with a top portion and a short cylindrical valve body member 38, the cylindrical interlocking member 33 with a top portion is slidably inserted externally to the upper side of the flange-shaped locking portion 29a of the coupling shaft 29 constituting the valve shaft 20, the short cylindrical valve body member 38 is coupled to the lower end opening of the interlocking member 33 by welding, press-fitting, caulking, or the like, and a space defined near the lower end portion of (the coupling shaft 29 of) the valve shaft 20 by (the interlocking member 33 and the valve body member 38 of) the valve body 32 is defined as a communication space 34.

The top portion 33b of the interlocking member 33 is provided with an insertion portion 33c having a short cylindrical surface through which the coupling shaft 29 is slidably inserted. Further, a lower end portion of the cylindrical portion 33a of the interlocking member 33 is bonded to a flange-shaped portion 38a provided on an outer peripheral portion of the valve body member 38 by welding or the like, and a plurality of (lateral) through holes 33u (see fig. 2 in particular) that communicate the valve chamber 14 with the communication space 34 are provided in the cylindrical portion 33a of the interlocking member 33.

On the other hand, the lower end surface of the valve body member 38 is an inverted truncated cone-shaped first valve body portion (truncated cone surface portion) 38b, the inverted truncated cone-shaped first valve body portion 38b is in contact with and separated from the valve seat 15 of the valve body 10 (from above) to open and close the valve port 16, and a communication passage 37 composed of a stepped vertical hole that communicates the valve port 16 with the communication space 34 is formed in the center of the valve body member 38. The communication space 34 side of the communication passage 37 is a port (second port) 36, and the port 36 is formed of a cylindrical surface having a diameter smaller than that of the port 16 of the valve body 10 and opened and closed by the second valve core portion 29b of the coupling shaft 29.

Here, the top portion 33b of the interlocking member 33 and the flange-shaped locking portion 29a of the connecting shaft 29 provided on the valve shaft 20 are set to have a clearance L a (described later in detail) of a predetermined size in the axis O direction (vertical direction) when the valve port 36 is closed by the second valve core portion 29b of the connecting shaft 29 (in other words, when the second valve core portion 29b of the connecting shaft 29 is seated on the valve seat (second valve seat) 35 provided at the upper end of the valve port (second valve port) 36).

A compression coil spring (urging member) 39 that constantly urges the valve element 32 in the valve closing direction (downward) is mounted in a compressed state between (a downward stepped surface of) the spring housing 19 and (the vicinity of the insertion portion 33c on the upper surface of the top portion 33b) of the interlocking member 33 constituting the valve element 32.

In addition to the above configuration, in the present embodiment, in order to narrow bubbles in the fluid (in the fluid flowing through a small flow passage described later), a sound deadening member (valve chamber 14 side sound deadening member) 71 made of a thin cylindrical metal mesh or the like is provided on the inner periphery of (the cylindrical portion 33a of) the interlocking member 33, and a sound deadening member (valve port 16 side sound deadening member) 72 made of a thin circular plate-shaped metal mesh or the like is also provided in the communication passage 37 of the valve body member 38.

Specifically, the muffler member 71 is disposed on the inner peripheral side of (the through hole 33u of) the interlocking member 33, the upper end of the muffler member 71 is fitted into a recess provided in (the lower surface edge of the top portion 33b of) the interlocking member 33, and the lower end of the muffler member 71 is sandwiched between (the outer peripheral upper end of) the valve body member 38 and (the lower end of) the interlocking member 33. Further, a pressure plate 73 (support member) having a plurality of (four in the illustrated example) through holes 73a is fixed to the step portion of the communication passage 37 of the valve body member 38 by caulking or the like (see fig. 3), and the muffler member 72 is held and fixed in the communication passage 37 of the valve body member 38 by sandwiching the muffler member 72 between the pressure plate 73 and the step portion of the communication passage 37 of the valve body member 38.

Here, although the metal mesh (net member) having a plurality of small holes is used as the

silencer members

71 and 72, if the bubbles in the fluid can be reduced, the

silencer members

71 and 72 may be made of resin, or the

silencer members

71 and 72 themselves may be formed of porous materials, for example.

It is to be understood that the number, diameter, and formation position of the through holes 33u of the interlocking member 33, the number, diameter, and formation position of the through holes 73a of the pressure plate 73, and the like are not limited to the illustrated example, and that the method of fixing the muffling

members

71, 72, and the like are not limited to the illustrated example.

In the flow rate control valve 1 configured as described above, the fluid (refrigerant) flows in two directions (two directions of a direction of flow from the inlet 11 to the outlet 12 (horizontal → downward, forward flow) and a direction of flow from the outlet 12 to the inlet 11 (downward → horizontal, reverse flow)), and the amount of rotation of the rotor 50 is controlled to change the amount of lift L of the valve shaft 20, thereby adjusting the flow rate of the fluid (refrigerant).

(operation of the flow control valve 1 in the forward flow)

In the normal flow, in the fully closed state (the state where the rising amount L of the valve shaft 20 is zero) shown in fig. 4 a, the second valve core portion 29b of (the coupling shaft 29 of) the valve shaft 20 is pressed (seated) against the valve seat 35 of (the valve body member 38 of) the valve body 32 to close the valve port 36, and the first valve body portion 38b of (the valve body member 38 of) the valve body 32 is pressed (seated) against the valve seat 15 of the valve body 10 to close the valve port 16. further, the check valve body 21 is urged by the compression coil spring 21a to close the check valve port 21v of (the coupling shaft 29 of) the valve shaft 20 (that is, the flow of the fluid from the valve chamber 14 to the valve port 16 is stopped by the check valve body 21). at this time, (the upper surface of) the flange-shaped locking portion 29a of (the coupling shaft 29 of) the valve shaft 20 and (the lower surface of) the top portion 33b of the interlocking member 33 of the valve body 32 are positioned at positions separated from the gap L a by.

In this fully closed state, when the valve shaft 20 is raised, as shown in fig. 4B, until the clearance (rise amount) of the predetermined size becomes L a (small flow rate control state), the first valve body portion 38B of the valve shaft 32 is pressed (seated) against the valve seat 15 of the valve body 10 by (the urging force of) the compression coil spring 39, and, in a state where the check valve body 21 is urged by (the urging force of) the compression coil spring 21a and the check valve port 21v of the valve shaft 20 is closed, the coupling shaft 29 of the valve shaft 20 moves (rises) within the insertion portion 33c of the top portion 33B of the interlocking member 33 of the valve shaft 32, and the second valve core portion 29B of the valve shaft 20 separates from the valve seat 35 of the valve shaft 32 and the valve port 36 opens, when the valve core portion 29B that flows into the valve chamber 14 from the valve seat 35 of the valve shaft 32 is forced to move (rise), and when the valve shaft portion 32B flows into the communication port 36 opens from the valve port 33a communication port 33a downstream side of the valve core portion 33a cylindrical portion 33 of the interlocking member 33 of the valve shaft 32, the valve shaft 32 is disposed from the communication port 33u → the communication space 34 to the communication port 37 of the valve shaft 32, and when the valve shaft portion 32 flows into the communication port 32 from the communication port 32 (the communication port 32) through the communication port 32, the communication port 32 is disposed from the communication port 32, and the communication port 32, the communication port 32 is disposed between the communication port 32, and the communication port 32 is disposed between the communication port 32, the communication port 32 is disposed in a noise is reduced when the communication port 32 is reduced when the flow rate of the flow of.

Here, a flow path that connects the valve chamber 14 and the valve port 16 via the following structure is referred to as a small flow path: the through hole 33u of the (cylindrical portion 33a of the) interlocking member 33 of the above-described valve body 32 → the communication space 34 → the clearance between the second core portion 29b of the valve shaft 20 and the valve seat 35 of the valve body 32 → the communication passage 37 (valve port 36) of the valve body member 38 of the valve body 32.

The rise L a is a rise L of the valve shaft 20 corresponding to a flow rate at which noise (fluid passing sound) is likely to occur when the fluid (refrigerant) passes through, and can be determined in advance based on experiments or the like.

When the valve shaft 20 is raised up to the rise L a and then the valve shaft 20 is further raised (that is, the rise L exceeds the rise L a), as shown in fig. 4C, the flange-shaped locking portion 29a of (the coupling shaft 29 of) the valve shaft 20 engages with the top portion 33b of (the interlocking member 33 of) the valve body 32, the valve body 32 moves (rises) together with (integrally with) the valve shaft 20 against the biasing force of the compression coil spring 39, the first valve body 38b of the valve body 32 is separated from the valve seat 15 of the valve body 10, a gap (flow path in the axial O direction) of the width L b (L-L a) (annular flow path) is formed between the first valve body 38b of the valve body 32 and the valve seat 15 of the valve body 10 (annular flow control state), fluid flowing from the inlet 11 to the valve chamber 14 flows into the gap between the first valve body 38b of the valve body 10 and the valve seat 15 of the valve body 10 via the gap (flow path) between the first valve body 38b of the valve body 32 and the valve seat 15 of the valve body 10, flows into the valve body 16 connected therebelow, the valve body 16, the fluid flows into the valve chamber 16, the inlet 16, the flow path is increased, and the fluid flows into the valve chamber 14, and flows into the flow path is formed by the flow path from the valve chamber 14, and the flow path is reduced directly into the valve chamber 14, and the flow path is formed by the flow path, and the flow path (flow path) of the flow path formed by the flow path of the valve body 14, the flow path of the flow path 14, the flow path of the flow.

It is to be noted that, when the valve shaft 20 is lowered from the fully opened state shown in fig. 4 (C), and the flow rate of the fluid flowing into the valve port 16 is reduced accordingly, it is needless to say that the same operational effects as described above can be obtained.

(operation in reverse flow of the flow control valve 1)

In the reverse flow, when the differential pressure between the valve port 16 side (outlet 12 side) and the valve chamber 14 side (inlet 11) is greater than a predetermined differential pressure (in other words, the pressure on the valve port 16 side is higher than the pressure on the valve chamber 14 side by a predetermined pressure) in the fully closed state (the state explained based on fig. 4 a) shown in fig. 5 a, as shown in fig. 5B, the second valve core portion 29B holding (the coupling shaft 29 of) the valve shaft 20 is pressed (seated) against the valve seat 35 of (the valve body 38 of) the valve body 32, the first valve body portion 38B of (the valve body 38 of) the valve body 32 is pressed (seated) against the seated valve seat 15 of the valve body 10, the check valve body 21 moves (rises) in the housing chamber 21B against the biasing force of the compression coil spring 21a, and the check valve port 21v of (the coupling shaft 29) of the valve shaft 20 is opened. The fluid flowing in from (the valve port 16 of) the outlet port 12 flows into the valve chamber 14 via the communication passage 37 (the valve port 36) of the valve body member 38 of the valve body 32 (particularly, the through hole 73a of the pressure plate 73 fixed to the communication passage 37) → the check valve port 21v of (the bottom portion of) the coupling shaft 29 of the valve shaft 20 → the housing chamber 21b → the communication port 21u → the communication space 34 → the through port 33u of (the cylindrical portion 33a of) the interlocking member 33 of the valve body 32. In this state, the opening area of the flow path through which the fluid that has flowed into the valve chamber 14 (i.e., the fluid that has flowed out to the inlet 11) flows is constant. At this time, the fluid flowing in from the outlet 12 passes through the muffler member 72 disposed in the communication passage 37 of the valve member 38 of the valve body 32 (when flowing from the valve port 16 into the communication passage 37 of the valve member 38), passes through the muffler member 71 disposed on the inner periphery of (the cylindrical portion 33a of) the interlocking member 33 (when flowing from the communication space 34 into the through-port 33u of the interlocking member 33 of the valve body 32), and passes through the valve chamber 14 (the inlet 11) in a state where bubbles in the thinned fluid are decomposed by the two

muffler members

72, 71 disposed on the upstream side (the valve port 16 side) and the downstream side (the valve chamber 14 side) of the valve port 36. Therefore, in a small flow rate control region (a region where noise is likely to occur), noise when the fluid (refrigerant) passes through is reliably reduced.

When the valve shaft 20 is raised in a state where the check valve port 21v is open, as shown in fig. 5C, the second valve core portion 29b of the valve shaft 20 is held in pressure contact with (seated on) the valve seat 35 of the valve body 32 (i.e., in a state where the flange-shaped locking portion 29a of the valve shaft 20 and the top portion 33b of the interlocking member 33 are located apart from the gap L a of a predetermined size in the direction of the axis O), the valve body 32 moves (rises) together with the valve shaft 20 (integrally) against the urging force of the compression coil spring 39 (i.e., the pressure of the fluid flowing into the valve chamber 14 from the valve port 16 overcomes the urging force of the compression coil spring 39), the first valve core portion 38b of the valve body 32 is separated from the valve seat 15 of the valve body 10, a gap (annular flow path) of width L (in the direction of the axis O) is formed between the first valve core portion 38b of the valve body 32 and the valve seat 15 of the valve body 10, and accordingly, the check valve body 21 moves in the housing chamber 21b by the urging force of the compression coil spring 21a flow path, the flow of the fluid flowing into the valve chamber 20 (inlet port 12) is increased, and the flow rate of the flow path is increased by the flow control valve body 14, and the flow loss of the flow flowing into the flow path is reduced directly caused by the flow rate of the flow flowing into the valve chamber 20 (i.e., when the flow rate of the flow path).

Thus, in the flow rate control valve 1 of the present embodiment, the silencing

members

71 and 72 that narrow bubbles in the fluid flowing through the small flow passage are disposed on the valve chamber 14 side (upstream side in the case of forward flow and downstream side in the case of reverse flow) and the valve port 16 side (downstream side in the case of forward flow and upstream side in the case of reverse flow) of the valve port (second valve port) 36 of the small flow passage that communicates the valve chamber 14 and the valve port (first valve port) 16 via the communication space 34, specifically, on the through port 33u of the interlocking member 33 of the valve body 32 and the communication passage 37 of the valve body member 38, and therefore, the noise when the fluid (refrigerant) passes can be effectively reduced, and the pressure loss in the large opening degree (large flow rate control) region is reduced, and an appropriate refrigerant flow rate can be obtained.

Although the fluid is allowed to flow from the valve port 16 to the valve chamber 14 in a state where the valve port 16 is closed by the first valve core portion 38b of the valve body 32 and the valve port 36 is closed by the second valve core portion 29b of the valve shaft 20, the check valve structure using the check valve body 21 that prevents the fluid from flowing from the valve chamber 14 to the valve port 16 is not limited to the above-described structure. For example, as shown in fig. 6 (a), the compression coil spring 21a attached between the check valve body 21 and the thrust transmission shaft 28 may be omitted. In this case, in order to limit the amount of movement of the check valve body 21 in the housing chamber 21b, a protruding portion 28a formed on the lower surface of the thrust transmission shaft 28 may be disposed close to the check valve body 21. In order to suppress the noise (collision noise) of the check valve body 21 disposed in the housing chamber 21B, for example, as shown in fig. 6 (B), a projecting portion 28a formed on the lower surface of the thrust transmission shaft 28 may be formed of another component such as a cushion material made of resin or rubber. For example, as shown in fig. 6C, the check valve body 21 may be formed into a stepped cylindrical shape (a cylindrical shape having an outer diameter substantially equal to the inner diameter of the connecting shaft 29) and a conical truncated-cone shape portion that opens and closes the check valve port 21v, and a pressure equalizing port 29d may be formed in (a cylindrical portion of) the connecting shaft 29 of the valve shaft 29, the pressure equalizing port 29d communicating the valve chamber 14 and the back surface side (the side opposite to the check valve port 21v side) of the check valve body 21 of the housing chamber 21 b.

In the above-described embodiment, the check valve body 21 is used to flow the fluid (refrigerant) in both the direction of flow from the inlet 11 to the outlet 12 (forward flow) and the direction of flow from the outlet 12 to the inlet 11 (reverse flow), but for example, when the check valve body 21 is applied to a system in which the fluid (refrigerant) flows only in one direction (the direction of flow from the inlet 11 to the outlet 12 (forward flow), that is, the direction in which the check valve body 21 does not function and the check valve port 21v is always closed by the check valve body 21), the coupling shaft 29 of the valve shaft 20 may be formed as a solid body (a columnar body with steps) as in the flow rate control valve 1A shown in fig. 7, and the check valve body 21 and the structures (the housing chamber 21b, the check valve port 21v, the receiving chamber 21b, the receiving chamber 21v, and the receiving chamber) attached to the check valve, The communication port 21 u). In fig. 7, the same reference numerals are given to the components having the same functions and actions as those of the above-described embodiment. Even with the flow rate control valve 1A having such a configuration, it is needless to say that the same operational effects as those of the flow rate control valve 1 of the above embodiment can be obtained.

In the above embodiment, the singular planetary gear reduction mechanism 60 that reduces the rotation speed of the rotor 50 is used, but for example, as in the flow rate control valve 1B shown in fig. 8, the singular planetary gear reduction mechanism may be omitted, the bellows 28B may be attached to the outer periphery of (the thrust transmission shaft 28 of) the valve shaft 20, the compression coil spring 39 as the biasing member that biases the valve body 32 in the valve closing direction (downward) may be provided between the annular upper spring holder 28Ba and the top portion 33B of the interlocking member 33 of the valve body 32, and the annular upper spring holder 28Ba may be sandwiched between (the stepped portion of) the thrust transmission shaft 28 and (the upper end portion of) the coupling shaft 29 (see patent document 2 for details). In fig. 8, the same reference numerals are given to the components having the same functions and actions as those of the above-described embodiment. Even in the flow rate control valve 1C having such a configuration, the same operational effects as those of the flow rate control valve 1 of the above embodiment can be obtained without detailed description.

In the above embodiment, the flow rate control valve can be configured without installing the compression coil spring 39. In this case, the valve body 32 is seated on the valve seat 15 or separated from the valve seat 15 mainly by hydraulic pressure.

The present invention is also directed to the electric flow rate control valve described in the above-described embodiment, in which the valve shaft is moved up and down (moved) by using a stepping motor or the like having a stator and a rotor to arbitrarily and finely control the amount of lift (valve opening degree), and it is needless to say that an electromagnetic flow rate control (switching) valve such as an electromagnet may be used.

Claims

1. A flow rate control valve is characterized by comprising:

a valve body provided with a valve chamber and a first valve port; a valve shaft disposed in the valve chamber so as to be vertically movable; an elevation drive unit for elevating the valve shaft; and a valve body slidably inserted around the valve shaft so as to surround the outer periphery of the lower end portion of the valve shaft and driven in conjunction with the lifting operation of the valve shaft,

the valve core is provided with a first valve core part which changes the flow of the fluid flowing through the first valve port according to the rising amount,

a small flow passage that communicates the valve chamber with the first port via a communication space defined by the valve body near a lower end portion of the valve shaft, and a second valve core portion that changes a flow rate of a fluid flowing through a second port provided in the small flow passage in accordance with an increase amount is provided in the valve shaft,

the flow rate control valve is configured to be in a small flow rate control state in which the first valve port is closed by the first valve core portion and a flow rate is controlled according to an amount of rise of the second valve core portion with respect to the second valve port when an amount of rise of the second valve core portion is equal to or less than a predetermined amount, and to be in a large flow rate control state in which the valve core is raised along with the rise of the valve shaft and the first valve port is opened by the first valve core portion when the amount of rise of the second valve core portion exceeds the predetermined amount,

the valve core is composed of a cylindrical interlocking component and a valve core component, the cylindrical interlocking component is provided with a top and is freely inserted outside the upper side of the second valve core part in the valve shaft in a sliding way, the valve core component is connected with the lower end opening of the interlocking component and is provided with the first valve core part,

the urging member abuts on the top portion to urge the interlocking member in a valve closing direction of the first valve port,

the interlocking member has a plurality of through-holes for communicating the valve chamber with the communication space,

a cylindrical valve chamber side silencing member is arranged on the inner periphery of the interlocking member,

a valve port side silencing member that thins bubbles in the fluid flowing through the small flow passage is disposed on the first valve port side of the second valve port in the small flow passage.

2. Flow regulating valve according to claim 1,

when the amount of lift of the second valve core portion exceeds the predetermined amount, the valve body is lifted by a flange-shaped locking portion provided on the valve shaft against the biasing force of the biasing member.

3. Flow regulating valve according to claim 1,

the small flow passage is constituted by the through port, the communication space, and a communication passage provided in the valve body member to communicate the communication space with the first valve port, and the second valve port is formed in the communication passage.

4. Flow regulating valve according to claim 3,

the cylindrical valve chamber side muffler member is disposed on the inner periphery of the interlocking member such that the upper end thereof is fitted into a recess provided in the interlocking member and the lower end thereof is sandwiched between the valve body member and the interlocking member.

5. Flow regulating valve according to claim 3 or 4,

the valve port-side muffler member supports the communication passage fixed to the valve body member by a support member having a through hole, and the support member is fixed to the communication passage of the valve body member.

6. Flow regulating valve according to one of claims 1 to 4,

in a state where the first valve port is closed by the first spool portion and the second valve port is closed by the second spool portion, fluid is allowed to flow from the first valve port to the valve chamber, but a check spool is provided that prevents fluid from flowing from the valve chamber to the first valve port.

7. Flow regulating valve according to claim 6,

the valve shaft is provided with: a housing chamber that houses the check valve body; a check valve port that communicates with the housing chamber and the first valve port and is opened and closed by the check valve body according to a differential pressure between the first valve port side and the valve chamber side; and a communication port that is always communicated with the housing chamber and the valve chamber.