CN114645961B - pressure regulating valve - Google Patents
pressure regulating valve Download PDFInfo
- Publication number
- CN114645961B CN114645961B CN202111478611.3A CN202111478611A CN114645961B CN 114645961 B CN114645961 B CN 114645961B CN 202111478611 A CN202111478611 A CN 202111478611A CN 114645961 B CN114645961 B CN 114645961B
- Authority
- CN
- China
- Prior art keywords
- pressure
- needle
- connecting member
- valve
- bellows
- 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.)
- Active
Links
- 230000001105 regulatory effect Effects 0.000 title claims abstract description 65
- 230000007246 mechanism Effects 0.000 claims abstract description 41
- 238000003780 insertion Methods 0.000 claims abstract description 22
- 230000037431 insertion Effects 0.000 claims abstract description 22
- 230000009471 action Effects 0.000 claims abstract description 8
- 230000008878 coupling Effects 0.000 claims description 12
- 238000010168 coupling process Methods 0.000 claims description 12
- 238000005859 coupling reaction Methods 0.000 claims description 12
- 230000002401 inhibitory effect Effects 0.000 abstract description 2
- 230000000694 effects Effects 0.000 description 7
- 230000009467 reduction Effects 0.000 description 7
- 229910052751 metal Inorganic materials 0.000 description 6
- 239000002184 metal Substances 0.000 description 6
- 229910001220 stainless steel Inorganic materials 0.000 description 6
- 239000010935 stainless steel Substances 0.000 description 6
- 230000002093 peripheral effect Effects 0.000 description 5
- 230000003252 repetitive effect Effects 0.000 description 5
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 4
- 239000004734 Polyphenylene sulfide Substances 0.000 description 4
- 230000000149 penetrating effect Effects 0.000 description 4
- 229920000069 polyphenylene sulfide Polymers 0.000 description 4
- 235000001674 Agaricus brunnescens Nutrition 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 239000010951 brass Substances 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 229910052742 iron Inorganic materials 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- NCGICGYLBXGBGN-UHFFFAOYSA-N 3-morpholin-4-yl-1-oxa-3-azonia-2-azanidacyclopent-3-en-5-imine;hydrochloride Chemical compound Cl.[N-]1OC(=N)C=[N+]1N1CCOCC1 NCGICGYLBXGBGN-UHFFFAOYSA-N 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
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
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/20—Excess-flow valves
- F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
-
- 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
- F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
- F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
- F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
- F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only spring-loaded
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Fluid Pressure (AREA)
- Safety Valves (AREA)
- Details Of Valves (AREA)
Abstract
The invention provides a pressure regulating valve with a pressure sensing bellows, which can reduce hysteresis by inhibiting inclination of a connecting rod in an insertion hole and sliding resistance caused by the connecting rod. In the pressure regulating valve (100 a), a connecting mechanism (80) for connecting the pressure sensing bellows unit (50) and the regulating spring unit (60) comprises: a lower engagement portion (81 c) provided at an axial center portion of the other end portion of the connecting rod (54); and a connecting member (83 b) having a spherical shape on a side portion thereof, the connecting member being in point contact with the sliding portion (53 c), wherein the lower portion of the connecting member (83 b) and the lower engaging portion (81 c) have one or the other of a concave shape and a protruding shape in the axial direction, respectively, and wherein concave-convex engagement having a centripetal action is formed, and wherein the first gap (CL 1) is made larger than the second gap (CL 2). As a result, the connecting rod (54) can eliminate inclination relative to the axial direction and increase of sliding resistance caused by the connecting rod, and hysteresis can be reduced.
Description
Technical Field
The present invention relates to a pressure regulating valve provided with a pressure-sensitive bellows.
Background
In the pressure regulating valve, in order to avoid the influence of the secondary side pressure, the valve opening is controlled by the fluctuation of the primary side pressure only by equalizing the effective pressure receiving diameter of the pressure-sensitive bellows to which the secondary side pressure is applied and the pressure receiving diameter of the valve portion, and by canceling the influence of the fluctuation of the secondary side pressure on the valve body.
Such a pressure regulating valve using a pressure-sensitive bellows (hereinafter referred to as "conventional pressure regulating valve") is shown in fig. 9, for example. In the conventional pressure regulating valve 200, an inflow pipe 201 and an outflow pipe 202 are connected to a valve housing 210, and a ball valve 240 is provided in a valve chamber 211 that communicates the inflow pipe 201 and the outflow pipe 202. In addition, the conventional pressure regulating valve 200 includes: a pressure-sensitive bellows unit 250 that biases the ball valve 240 in a valve closing direction, and an adjustment spring unit 260; and a rectifying element unit 290 that biases the ball valve 240 in a valve opening direction (see patent document 1). Here, the pressure-sensitive bellows unit 250 is constituted by a pressure-sensitive bellows 251, a bellows lower cover 252, a bellows upper cover 253, and a connecting rod 254. The adjustment spring unit 260 is composed of a spring seat member 261, an adjustment spring member 262, and an adjustment spring 263 sandwiched between the spring seat member 261 and the adjustment spring member 262.
Prior art literature
Patent literature
Patent document 1: japanese patent laid-open No. 6-229481
Disclosure of Invention
Problems to be solved by the invention
First, the pressure-sensitive bellows unit 250 and the adjustment spring unit 260 are engaged with each other via the connecting rod 254. One end portion and the other end portion of the connecting rod 254 are fitted to the bellows lower cover 252 and the spring seat member 261, which are movable in the radial direction, via the first guide vane 255 and the second guide vane 265, which are elastic members, respectively. The central portion of the connecting rod 254 is inserted into an insertion hole 253a provided in the bellows upper cover 253, but a small gap is set between the connecting rod 254 and the insertion hole 253 a. Through the minute gap, the atmospheric pressure is introduced into the internal space of the pressure-sensing bellows 251, while the secondary pressure P2 is introduced into the external space of the pressure-sensing bellows 251. Further, the rectifying element unit 290 transmits the force of the adjustment spring 292 to the ball valve 240 via the rectifying element 291.
Therefore, the conventional pressure regulating valve 200 may tilt and decenter the connecting rod 254 with respect to the center axis C mainly for the following two reasons. First, the adjustment spring 263 is non-linearly arranged in a state of being slightly bent or inclined with respect to the central axis C, thereby having non-linearity (hereinafter referred to as "non-linearity of the adjustment spring"). Due to the nonlinearity of the adjustment spring 263, the force not along the center axis C is transmitted to the link 254. Second, the pressure-sensitive bellows 251 has asymmetry (hereinafter referred to as "asymmetry of the pressure-sensitive bellows") due to, for example, minute thickness unevenness caused by expansion molding. Due to the asymmetry of the pressure-sensitive bellows 251, a force not along the central axis C is applied to the connecting rod 254.
For these reasons, in the conventional pressure adjustment valve 200, if the connecting rod 254 is inclined or eccentric with respect to the center axis C, the contact area is large due to the line contact, and thus a problem (hereinafter referred to as "conventional problem point (increase in sliding resistance)") of increasing the sliding resistance with the insertion hole 253a occurs, and hysteresis becomes large.
The invention aims to provide a pressure regulating valve with a pressure sensing corrugated pipe, which can reduce hysteresis by inhibiting inclination of a connecting rod in an insertion hole and sliding resistance caused by the connecting rod.
Means for solving the problems
In order to solve the above problem, a pressure regulating valve includes: a valve body having a valve seat; a needle having a valve portion that can be moved toward and away from the valve seat; a pressure-sensitive bellows unit having a pressure-sensitive bellows that expands and contracts in an axial direction; an adjustment spring unit having an adjustment spring for biasing the valve portion in a valve closing direction; and a connection mechanism that connects the pressure-sensitive bellows unit and the adjustment spring unit, the pressure-sensitive bellows unit including: the bellows cover on the side of the adjusting spring unit is provided with an inserting hole and a sliding part which are communicated along the axial direction; a bellows cover on the needle side; the pressure-sensitive bellows is connected to the bellows cap at the needle-side end, and is fixed so as not to be displaced relative to the valve body at the adjustment spring unit-side end; and a connecting rod configured such that the end on the needle side is connected to the bellows cover on the needle side, and the end on the adjustment spring unit side is insertable into the insertion hole and the sliding portion, the connecting mechanism including: an engaging portion provided at an axial center portion of the end portion of the connecting rod on the side of the adjustment spring unit; and a connecting member having a spherical shape on a side portion thereof, the connecting member having one or the other of a concave shape and a convex shape in an axial direction, the end portion of the needle side and the engaging portion having a point contact with the sliding portion, respectively, the connecting member being formed with a concave-convex engagement having a centripetal action such that a first gap formed between the connecting rod and the insertion hole is larger than a second gap formed between the connecting member and the sliding portion.
In the pressure regulating valve, a third gap formed between the connecting rod and the valley portion of the pressure-sensitive bellows may be larger than a gap obtained by adding a fourth gap formed by the connection between the end portion of the connecting rod on the needle side and the bellows cover on the needle side to the second gap.
In the pressure adjustment valve, a side portion of the connecting member that is in point contact with the sliding portion may be an outermost diameter portion of the connecting member when viewed from the axial direction.
In the pressure regulating valve, a sliding region length from a point contact position of the sliding portion and a side portion of the connecting member to an end portion of the sliding portion on the regulating spring unit side in a valve-closed state of the pressure regulating valve may be set to be larger than a maximum lift amount of the needle.
In the pressure regulating valve, the needle-side end of the regulating spring may be directly abutted against the connecting member, and the regulating spring may be inserted into the sliding portion in a non-contact state.
In the pressure regulating valve, the engagement portion may have a conical shape, and the end portion of the connecting member may have a spherical shape, wherein a vertex angle θ of the conical shape of the engagement portion satisfies θ > 180-2×sin using a radius Ra of the spherical shape of the end portion of the connecting member on the needle side and a radius Rb of the bottom surface of the conical shape of the engagement portion -1 (Rb/Ra)。
In the pressure adjustment valve, the shape of the engagement portion and the shape of the needle-side end portion of the connecting member may be spherical, and the radius of the spherical shape of the engagement portion may be larger than the radius of the spherical shape of the needle-side end portion of the connecting member.
In the pressure regulating valve, the shape of the engagement portion and the shape of the needle-side end portion of the connecting member may be tapered such that the apex angle of the tapered shape of the engagement portion is larger than the apex angle of the tapered shape of the needle-side end portion of the connecting member.
Effects of the invention
According to the present invention, it is possible to provide a pressure regulating valve including a pressure-sensitive bellows, which can reduce hysteresis by suppressing inclination of a connecting rod in an insertion hole and sliding resistance caused by the connecting rod.
Drawings
Fig. 1 is a cross-sectional view showing a closed state of a pressure regulating valve according to a first embodiment of the present invention.
Fig. 2 is an enlarged view showing a main portion of fig. 1.
Fig. 3 is an enlarged view showing the upper connection mechanism of fig. 2, (a) is a partially enlarged view surrounded by a broken line III of fig. 2, and (b) is a schematic view showing a contact state between the spherical connection member and the conical lower engagement portion in (a).
Fig. 4 is a partially enlarged view of an upper connection mechanism in the pressure adjustment valve of the second embodiment.
Fig. 5 is a partially enlarged view of an upper connection mechanism in the pressure regulating valve of the third embodiment.
Fig. 6 is a partially enlarged view of an upper connection mechanism in the pressure adjustment valve of the fourth embodiment.
Fig. 7 is a partially enlarged view of an upper connection mechanism in the pressure regulating valve of the fifth embodiment.
Fig. 8 is a partially enlarged view of an upper connection mechanism in the pressure adjustment valve of the sixth embodiment.
Fig. 9 is a cross-sectional view showing a closed state of a pressure regulating valve provided with a pressure-sensitive bellows according to the related art.
In the figure:
100a to 100f, a pressure regulating valve, 5-valve body, 10-valve housing, 11-inlet port, 12-outlet port, 13-needle guide hole, 14-needle housing chamber, 15-valve chamber, 16-bellows housing chamber, 18-valve seat, 20-connecting member, 30-spring housing, 40-needle, 41-guide portion, 42-valve portion, 44-internal flow path, 50-pressure sensing bellows unit, 51-pressure sensing bellows, 52-bellows lower cover, 53-bellows upper cover, 54-connecting rod, 60-regulating spring unit, 61-spring seat member, 62-regulating spring member, 63-regulating spring, 70-lower connecting mechanism, 71-lower side concave portion, 72-upper side concave portion, 73-ball, 80 a-80 f-upper connection (connection), 81C, 81 s-lower engagement, 82C-upper engagement, 83b, 83 m-connection, 84C, 84 s-spring seat connection (connection), C-center axis, CL 1-first gap, CL 2-second gap, CL 3-third gap, L1-sliding area length, L2-maximum lift, ra-spherical radius of connection, rb-conical bottom radius of lower engagement, rc-spherical radius of lower engagement, θ -apex angle of conical lower engagement.
Detailed Description
An embodiment of the present invention will be described in detail with reference to fig. 1 to 8. However, the present invention is not limited to the embodiment.
< related terms >
In the description of the present specification, "upper" and "lower" mean "adjustment spring unit side" and "needle side". In the description of the present specification and claims, the "effective pressure receiving area of the pressure-sensitive bellows" means a pressure receiving area calculated as an approximate value based on the average inner diameter of the minimum inner diameter (inner diameter of the "valley" portion of the bellows shape protruding toward the central axis side of the pressure-sensitive bellows) and the maximum inner diameter (inner diameter of the "mountain" portion of the bellows shape protruding toward the central axis side of the pressure-sensitive bellows) of the bellows shape. Further, in the description of the present specification and claims, "guidable" means "slidable". In the description of the present specification and claims, "concave-convex engagement" means engagement of a shape recessed in the axial direction and a shape protruding in the axial direction, respectively.
(first embodiment)
Structure related to pressure regulating valve
A pressure regulating valve 100a according to a first embodiment of the present invention will be described with reference to fig. 1 and 2. The pressure regulating valve 100a is mainly composed of a valve body 5, a needle 40, a pressure-sensing bellows unit 50, and a regulating spring unit 60. The respective configurations of the pressure regulating valve 100a will be described in order. In the pressure regulating valve 100a, the needle 40, the pressure-sensitive bellows unit 50, and the regulating spring unit 60 are assembled to the valve body 5 in an indirectly engaged state from one end side to the other end side. Here, the pressure adjusting valve 100a of the present embodiment is provided with the upper connecting mechanism 80 between the axially facing surfaces of the connecting rod 54 and the adjusting spring unit 60, as will be described in detail later. The upper connection mechanism 80 suppresses the inclination of the connecting rod 54 with respect to the center axis C and the sliding resistance of the connection member 83 in the sliding portion 53C, and thus can eliminate the conventional problem (increase in sliding resistance) and reduce hysteresis.
The valve body 5 is composed of a valve housing 10 connected to the inflow pipe 1 and the outflow pipe 2, a connecting member 20 joined by brazing after being pressed into the other end portion of the valve housing 10, and a spring case 30 joined to the other end portion of the connecting member 20 by caulking or the like. The valve body 5 is made of a metal such as brass, iron, aluminum, or stainless steel, or a resin material such as polyphenylene sulfide (PPS), or the like.
The valve housing 10 is a hollow cylindrical member having a through hole penetrating along the central axis C, and an inlet port 11, a needle guide hole 13, a needle accommodating chamber 14, a valve chamber 15, and a bellows accommodating chamber 16 connected to the inflow tube 1 are provided in the through hole so as to communicate with each other. The needle guide hole 13 is set to have a smaller inner diameter than the needle accommodating chamber 14, and an annular stepped portion 17 is provided at a connecting portion between the needle guide hole 13 and the needle accommodating chamber 14. The valve chamber 15 is set to have an inner diameter larger than that of the needle accommodating chamber 14, and an annular valve seat 18 is provided at a connecting portion between the valve chamber 15 and the needle accommodating chamber 14.
The valve housing 10 further has a through hole penetrating in the radial direction from the valve chamber 15, and an outlet port 12 connected to the outflow pipe 2 is provided in the through hole. The structure is as follows: in the closed state, the secondary side pressure P2 can be introduced into the valve chamber 15 and the bellows accommodating chamber 16 through the outlet port 12.
The coupling member 20 is a hollow cylindrical member having a through hole penetrating along the central axis C, has substantially the same inner diameter as the bellows accommodating chamber 16, and has an opening 21 continuously connected to the bellows accommodating chamber 16. In the present embodiment, the coupling member 20 is separate from the valve housing 10, but the present invention is not limited to this, and may be integrated.
The spring housing 30 is a hollow cylindrical member having a through hole penetrating along the central axis C, and is provided with a spring housing chamber 31. Further, a female screw portion 32 is provided on the inner peripheral side of the other end portion of the spring housing 30, and the female screw portion 32 is screwed with a male screw portion 62a provided on the outer peripheral side of the adjustment spring member 62 so as to be movable in the axial direction.
Next, the needle 40 will be described. As shown in fig. 2, the needle 40 includes: a cylindrical guide portion 41 extending toward one axial end; a substantially truncated cone-shaped valve portion 42 provided at the other end side; and an annular spring support portion 43 provided between the guide portion 41 and the valve portion 42. The needle 40 has an internal flow path 44, and the internal flow path 44 extends along the central axis C in the guide portion 41 and penetrates the valve portion 42 in the radial direction. The needle 40 is made of a metal such as stainless steel.
The guide portion 41 of the needle 40 is disposed so as to be axially guided in the needle guide hole 13 of the valve housing 10. Here, the clearance between the outer diameter of the guide portion 41 and the inner diameter of the needle guide hole 13 is set to be small, and tight tolerance control is performed. The needle 40 is always biased in the valve opening direction by the valve spring 6 sandwiched between the spring support portion 43 of the needle 40 and the stepped portion 17 of the valve housing 10. Thus, since the needle 40 is guided in a stable state in the axial direction, and the central positions of the needle 40 and the valve seat 18 are always aligned as viewed from the central axis C direction, the flow rate instability and the valve leakage can be improved.
The movement of the needle 40 in the axial direction is generated by a pressure difference between the primary side pressure P1 and the secondary side pressure P2, the biasing force of the pressure-sensitive bellows 51 and the adjustment spring 63 acting on the other end portion of the valve portion 42, the biasing force of the valve spring 6 acting on the spring support portion 43, and the like, which will be described in detail later. By these external forces, the valve portion 42 can move closer to or farther from the valve seat 18, and the valve opening degree is determined. Further, as will be described in detail later, the stepped portion 54c of the connecting rod 54 is in contact with the bellows upper cover 53, whereby the maximum lifted state of the maximum lift amount L2 of the needle 40 can be defined.
Next, the pressure-sensitive bellows unit 50 will be described. The pressure-sensitive bellows unit 50 is composed of a pressure-sensitive bellows 51, a bellows lower cover 52 (a bellows cover on the needle 40 side), a bellows upper cover 53 (a bellows cover on the adjustment spring unit 60 side), and a coupling lever 54. The pressure-sensitive bellows 51 has one end and the other end extending along the central axis C connected to a bellows lower cover 52 and a bellows upper cover 53, respectively, and biases the valve portion 42 in the valve closing direction. The connecting rod 54 has one end portion and the other end portion extending along the central axis C. The pressure-sensitive bellows unit 50 is made of metal such as stainless steel, and is accommodated in the bellows accommodating chamber 16 of the valve housing 10 and the opening 21 of the coupling member 20.
The pressure-sensing bellows 51 is connected to the bellows lower cover 52 and the bellows upper cover 53, respectively, and thereby the secondary side pressure P2 is always introduced into the external space of the pressure-sensing bellows 51 through the valve chamber 15 and the bellows accommodating chamber 16. On the other hand, as will be described in detail later, the atmosphere is always introduced into the internal space of the pressure-sensitive bellows 51 through the first clearance CL1 (see fig. 3 a) formed between the small diameter portion 54b of the connecting rod 54 and the insertion hole 53a of the bellows upper cover 53, and the second clearance CL2 (see fig. 3 a) formed between the connecting member 83 and the sliding portion 53c of the bellows upper cover 53. The pressure-sensitive bellows 51 is set in a dimensional relationship with the valve housing 10 and the connecting rod 54 so as to be always in a non-contact state.
The connecting rod 54 includes: a large diameter portion 54a of a substantially cylindrical shape extending toward one end side in the axial direction; and a small diameter portion 54b of a substantially cylindrical shape extending from the large diameter portion 54a toward the other end side in the axial direction. A recess 54ar is formed at one end of the large diameter portion 54 a. An annular stepped portion 54c is formed between the large diameter portion 54a and the small diameter portion 54b.
The bellows upper cover 53 includes: an insertion hole 53a extending concentrically along the central axis C and inserted through the small diameter portion 54b of the connecting rod 54; a bellows upper cover joint portion 53b to which the other end portion of the pressure-sensitive bellows 51 is connected; and a cylindrical sliding portion 53C having an inner diameter larger than the insertion hole 53a, extending concentrically along the central axis C, and sliding the connecting member 83. Here, the pressure-sensitive bellows unit 50 is fixed to the valve body 5 via the welded portion W so as not to be displaced relative to each other. The welded portion W represents a region where the bellows upper cover 53 and the other end portion of the coupling member 20 are welded to each other. By adjusting the axial position of the welded portion W, individual differences in the length of the pressure-sensitive bellows unit 50, assembly errors to the valve body 5, and the like can be absorbed. In the present embodiment, the inner diameter of the sliding portion 53c is set to be larger than the inner diameter of the insertion hole 53a, but the present invention is not limited thereto, and for example, the inner diameters of the sliding portion 53c and the insertion hole 53a may be set to be the same.
The bellows lower cover 52 includes a protruding portion 52a extending toward the other end side and a bellows lower cover joint portion 52b to which one end portion of the pressure-sensitive bellows 51 is connected. The convex portion 52a is inserted into the concave portion 54ar of the connecting rod 54, but since the outer diameter of the convex portion 52a is set smaller than the inner diameter of the concave portion 54ar of the connecting rod 54, the convex portion 52a is connected to the concave portion 54ar so as to be movable in the radial direction. A gap formed by the connection between the bellows lower cover 53 and the connecting rod 54 and movable in the radial direction is set as a fourth gap CL4. As described above, in the present embodiment, the bellows lower cover 52 and the connecting rod 54 are connected so as to be movable in the radial direction without being fixed to each other, and therefore, the inclination of the connecting rod 54 with respect to the central axis C, the asymmetry of the pressure-sensitive bellows 51, and the like can be absorbed. In addition, in the absence and irrespective of the inclination of the connecting rod 54 with respect to the central axis C or the asymmetry of the pressure-sensitive bellows 51, the connection (cl4=0) may be made without a gap between the convex portion 52a of the bellows lower cover joint portion and the concave portion 54ar of the connecting rod 54.
In the present embodiment, the pressure-sensitive bellows 51, the bellows lower cover 52, and the bellows upper cover 53 are separately provided, but the present invention is not limited thereto. For example, as the pressure-sensitive bellows 51 and the bellows lower cover 52, a pressure-sensitive bellows 51 having a cover-shaped lower end portion may be used, and the pressure-sensitive bellows 51 and the bellows lower cover 52 may be integrally connected. For example, as for the pressure-sensitive bellows 51 and the bellows upper cover 53, a pressure-sensitive bellows 51 having a flange-shaped upper end portion may be used, and an outer edge of the upper end portion of the pressure-sensitive bellows 51 may be fixed to an inner wall of the coupling member 20 (or the valve housing 10 integrated with the coupling member 20) as the valve body 5 so as not to be relatively displaced, and the coupling member 20 (or the valve housing 10) may be used as the bellows upper cover 53. In this way, when the upper end portion of the pressure-sensitive bellows 51 is fixed to the inner wall of the coupling member 20 (or the valve housing 10), the insertion hole 53a and the sliding portion 53c of the bellows upper cover 53 are formed in the inner wall of the coupling member 20 (or the valve housing 10).
Further, the adjustment spring unit 60 will be described. The adjustment spring unit 60 is composed of a spring seat member 61, an adjustment spring member 62, and an adjustment spring 63 interposed between the spring seat member 61 and the adjustment spring member 62 and biasing the valve portion 42 in the valve closing direction. The adjustment spring unit 60 is made of a metal such as brass, iron, aluminum, or stainless steel, or a resin material such as polyphenylene sulfide (PPS), and is accommodated in the spring accommodating chamber 31 of the spring housing 30. By screwing the male screw 62a provided on the outer peripheral side of the adjustment spring member 62 and the female screw 32 provided on the inner peripheral side of the other end portion of the spring housing 30, the force of the adjustment spring 63 can be adjusted by moving the adjustment spring member 62 in the axial direction, and the valve opening pressure (set value) of the needle 40 can be adjusted.
In the pressure regulating valve 100a of the present embodiment, the lower connection mechanism 70 and the upper connection mechanism 80 are disposed between the axially facing surfaces of the needle 40 and the pressure-sensitive bellows unit 50, and between the axially facing surfaces of the connecting rod 54 and the regulating spring unit 60, respectively.
The lower connection mechanism 70 is constituted by a pair of concave portions 71 and 72 formed on axially facing surfaces of the needle 40 and the pressure-sensitive bellows unit 50, and a ball 73 sandwiched between the pair of concave portions 71 and 72. The pair of concave portions 71, 72 are formed in the upper end surface of the valve portion 42 and the axial center portion of the lower end surface of the bellows lower cover 52, and are constituted by a conical lower concave portion 71 and an upper concave portion 72. The conical shape has a bottom surface formed as a circle concentric with the central axis C and an apex located on the central axis C. The ball 73 is made of metal such as stainless steel.
Accordingly, since the needle 40 can be disposed in the needle guide hole 13 of the valve housing 10 so as to be guided along the central axis C, the center position of the lower concave portion 71 is always located on the central axis C. Further, since the centripetal force acts on the upper concave portion 72 through the lower concave portion 71 and the ball 73, the center position of the upper concave portion 72 is autonomously arranged on the center axis C. This can suppress transmission of the force, which is not transmitted along the central axis C, to the needle 40 due to asymmetry or the like of the pressure-sensitive bellows 51, and can reduce the sliding resistance of the needle 40. In the present embodiment, the lower concave portion 71 and the upper concave portion 72 each have a conical shape, but the present invention is not limited thereto, and may have a spherical shape, for example.
< about upper connection mechanism >)
Here, the pressure regulating valve 100a of the present embodiment includes the pressure-sensitive bellows 51 and the regulating spring 63, similarly to the conventional pressure regulating valve 200. Therefore, the coupling rod 54 is inclined with respect to the center axis C due to the asymmetry of the pressure-sensitive bellows 51 and the nonlinearity of the adjustment spring 63, and there is a possibility that a conventional problem (increase in sliding resistance) occurs and hysteresis increases.
Therefore, in the pressure adjustment valve 100a of the present embodiment, the upper connecting mechanism (connecting mechanism) 80 is disposed between the axially facing surfaces of the connecting rod 54 and the adjustment spring unit 60, and the inclination of the connecting rod 54 with respect to the center axis C and the sliding resistance of the connecting member 83 of the sliding portion 53C are suppressed, so that the conventional problem (increase in sliding resistance) is eliminated, and hysteresis is reduced.
The upper connection mechanism 80 includes: a lower engaging portion 81 formed on an upper end surface of the connecting rod 54 (an engaging portion of the other end portion of the connecting rod 54 on the side of the adjustment spring unit 60); an upper engaging portion 82 formed on the lower end surface of the adjustment spring unit 60; and a connecting member 83 made of metal such as stainless steel sandwiched between the lower engaging portion 81 and the upper engaging portion 82.
Here, as shown in fig. 2, in the first embodiment, the upper connection mechanism 80 is constituted by a first upper connection mechanism 80 a. In the first embodiment, the lower engaging portion 81 and the upper engaging portion 82 are constituted by the lower engaging portion 81c and the upper engaging portion 82 c. Further, in the first embodiment, the connection member 83 is constituted by the connection member 83 b. The lower engaging portion 81c and the upper engaging portion 82c are formed in the upper end surface of the connecting rod 54 and the axial center portion of the lower end surface of the spring seat member 61, respectively, and have conical shapes. The conical shape has a bottom surface formed as a circle concentric with the central axis C and an apex located on the central axis C. In addition, the connecting member 83 has a ball shape.
Since the radius Ra of the connecting member 83b is set to be slightly smaller than the radius of the sliding portion 53c, an extremely narrow second clearance CL2 is formed between the side portion 83bs of the connecting member 83b and the sliding portion 53 c. Accordingly, since the movement of the connecting member 83b in the radial direction is regulated by the sliding portion 53C, the center position of the connecting member 83b is always disposed near the center axis C. Further, the side portion of the connecting member 83b that is in point contact with the sliding portion 53C is the outermost diameter portion of the connecting member 83b when viewed from the direction of the central axis C, and therefore the connecting member 83b can slide along the central axis C in a state where no change in sliding resistance occurs.
< centripetal action and contact State >
First, since the upper portion 83bu of the connecting member 83b whose movement in the radial direction is restricted acts centripetally on the upper engaging portion 82C, the center position of the conical upper engaging portion 82C is autonomously disposed in the vicinity of the central axis C. The conical upper engaging portion 82c and the spherical connecting member 83b are engaged with each other in a concave-convex manner, and have an annular contact line. This can improve the linearity of the adjustment spring 63. Further, even if the urging force not along the central axis C due to the nonlinearity of the adjustment spring 63 is applied to the connecting member 83b via the upper engaging portion 82C, the sliding resistance can be made small because the connecting member 83b is in a point contact state with respect to the sliding portion 53C of the bellows upper cover 53.
Next, since the downward engaging portion 81C is acted on centripetally via the lower portion 83bd of the connecting member 83b whose movement in the radial direction is restricted, the center position of the conical lower engaging portion 81C is autonomously arranged in the vicinity of the central axis C. The conical lower engaging portion 81c and the spherical connecting member 83b are engaged with each other in a concave-convex manner, and have an annular contact line. This can suppress the connecting rod 54 from tilting with respect to the center axis C. Here, the first clearance CL1 formed between the small diameter portion 54b of the connecting rod 54 and the insertion hole 53a of the bellows upper cover 53 is set to be larger than the second clearance CL2 formed between the side portion 83bs of the connecting member 83b and the sliding portion 53c of the bellows upper cover 53 (CL 1 > CL 2). Accordingly, the small diameter portion 54b of the connecting rod 54 is inserted into the insertion hole 53a along the central axis C in a non-contact state, and thus the sliding resistance between the small diameter portion 54b of the connecting rod 54 and the insertion hole 53a can be eliminated.
As described above, the first upper connection mechanism 80a according to the present embodiment can suppress the inclination of the connecting rod 54 with respect to the central axis C, and can be brought into a point contact state and a non-contact state with respect to the sliding portion 53C and the insertion hole 53a, respectively. This can eliminate the conventional problem (referred to as "increase in sliding resistance") and reduce hysteresis.
In the present embodiment, the third clearance CL3 formed between the large diameter portion 54a of the connecting rod 54 and the bellows-shaped valley portion protruding toward the central axis C of the pressure-sensitive bellows 51 is set to be larger than the clearance CL3 > cl2+cl4 formed by adding the second clearance CL2 formed between the side portion 83bs of the connecting member 83b and the sliding portion 53C of the bellows upper cover 53 and the fourth clearance CL4 formed by the connection between the convex portion 52a of the bellows lower cover 52 and the concave portion 54ar of the connecting rod 54. Accordingly, the large diameter portion 54a of the connecting rod 54 is inserted into the pressure-sensitive bellows 51 along the central axis C in a non-contact state, and therefore, breakage of the pressure-sensitive bellows 51 due to contact between the connecting rod 54 and the pressure-sensitive bellows 51 can be prevented. Note that, when the protruding portion 52a of the bellows lower cap joint portion is connected to the recessed portion 54ar of the connecting rod 54 without a gap therebetween (cl4=0), CL3 > CL2 may be set. In the present embodiment, the connecting rod 54 and the bellows lower cover 52 are connected by being separated from each other, but the connecting rod 54 and the bellows lower cover 52 may be connected by being integrally formed, and in this case, CL3 > CL2 may be set.
Further, in the present embodiment, the sliding region length L1 from the point contact position of the sliding portion 53c and the side portion 83bs of the connecting member 83b to the upper end portion of the sliding portion 53c in the closed valve state of the pressure regulating valve 100a is set to be larger than the maximum lift amount L2 of the needle 40 formed between the stepped portion 54c of the connecting rod 54 and the bellows upper cover 53 (L1 > L2). Thus, even when the pressure regulating valve 100a is in the fully opened valve state, the connecting member 83b can be kept from falling off the sliding portion 53 c.
Conditions for preventing the annular edge from abutting against the connecting member
The condition that the annular edge portions E1 and E2 are not brought into contact with the connecting member 83b will be described with reference to fig. 3 (b). First, straight lines are drawn from the centers O of the annular edge portions E1 and E2 of the belt connecting member 83b formed on the upper end outer peripheral portion of the lower engaging portion 81c, respectively, and the angle formed by +.e1oe 2 is set to α. The angle alpha formed by the +.E1OE2 is 2×sin -1 (Rb/Ra) calculation. Here, ra represents the radius of the connecting member 83b, and Rb represents the radius of the conical bottom surface of the lower engaging portion 81 c. The apex of the conical shape of the lower engaging portion 81c is denoted by O1, and the apex angle formed by +.e1o1e2 is denoted by θ.
Here, for example, when θ=180—α, the sum of the angle formed by the angle OE1O1 and the angle formed by the angle OE2O1 is 180 (°), that is, the angle formed by the angle OE1O1 and the angle formed by the angle OE2O1 are 90 (°), respectively, and therefore, the annular edge portions E1, E2 are the contact points of the connecting member 83b. Therefore, in the present embodiment, by satisfying the following expression (1), the contact position of the connecting member 83b with respect to the conical lower engaging portion 81c can be set on the conical surface on the side of the apex O1 excluding the annular edge portions E1, E2. As a result, the annular edge portions E1 and E2 can be prevented from abutting the spherical connecting member 83b.
Theta > 180-alpha (1)
(1) theta is more than 180-2 xSin -1 (Rb/Ra). Accordingly, by setting the radius Ra of the connecting member 83b and the radius Rb of the bottom surface of the conical shape of the lower engaging portion 81c so that the apex angle θ of the conical shape of the lower engaging portion 81c satisfies (expression 1), suppression can be achievedThe annular edge portions E1 and E2 are deformed or rubbed by the connecting member 83b, and the load of the adjustment spring 63 is changed, whereby the pressure (set value) at which the needle 40 opens the valve is changed. In the present embodiment, (formula 1) is used as a condition that the annular edge portions E1 and E2 of the lower engaging portion 81c are not in contact with the connecting member 83b, but is not limited thereto, and may be used as a condition that the annular edge portions E1 and E2 of the upper engaging portion 82c are not in contact with the connecting member 83b, for example.
< action on pressure regulating valve >)
The operation of the pressure control valve 100a will be described. Here, the refrigerant circuit will be described as the object of using the pressure adjustment valve 100a, but the present invention is not limited thereto. In the pressure regulating valve 100a, an inlet port 11 is connected to the high-pressure (primary side pressure P1) side inflow pipe 1, and an outlet port 12 is connected to the low-pressure (secondary side pressure P2) side outflow pipe 2.
(case where the primary side pressure P1 is lower than the set value)
When the primary pressure P1 is lower than the set value (for example, a state where the discharge pressure of the compressor is reduced, etc.), the valve portion 42 is seated on the valve seat 18 in a valve-closed state as shown in fig. 2. At this time, the secondary pressure P2 is introduced into the external space of the pressure-sensitive bellows 51 as the bellows accommodating chamber 16 through the valve chamber 15.
First, the pressure-sensing bellows 51 generates a secondary side pressure p2×an effective pressure receiving area S1 as a pressure acting in a valve opening direction of the valve portion 42. Here, the effective pressure receiving area S1 of the pressure-sensing bellows 51 is a pressure receiving area calculated based on the average inner diameters of the minimum inner diameter and the maximum inner diameter of the bellows shape.
Next, the needle 40 generates the primary side pressure p1×the pressure receiving area S2 as a pressure acting in the valve opening direction of the valve portion 42, and generates the secondary side pressure p2×the pressure receiving area S2 as a pressure acting in the valve closing direction of the valve portion 42. Further, the needle 40 is loaded with the biasing force F1 of the pressure-sensitive bellows 51 and the biasing force F2 of the adjustment spring 63 as forces acting in the valve closing direction of the valve portion 42. The needle 40 is loaded with the biasing force of the valve spring 6 as a force acting in the valve opening direction of the valve portion 42. The biasing force of the valve spring 6 is such as to cancel the dead weight of the needle 40, and therefore the following (expression 2) is not introduced.
Accordingly, the balance of the external force acting on the needle 40 of the pressure regulating valve 100a can be expressed as follows.
P2×s1+p1×s2=p2×s2+f1+f2 (formula 2)
Here, P1 is the primary side pressure [ N/mm ] 2 ]P2 is the secondary side pressure [ N/mm ] 2 ]S1 is the effective pressure receiving area [ mm ] of the pressure-sensitive bellows 51 2 ]S2 is the pressure receiving area [ mm ] of the valve portion 42 surrounded by the valve seat 18 2 ]F1 is the acting force [ N ] of the pressure-sensitive bellows 51]F2 is the force [ N ] of the adjusting spring 63]。
(formula 2) can be sorted into p2×s1+p1×s2-p2×s2=f1+f2. Here, the effective pressure receiving area S1 of the pressure-sensing bellows 51 is set to coincide with the pressure receiving area S2 of the valve portion 42 surrounded by the valve seat 18.
Therefore, in (equation 2), the external force applied to the needle 40 by the secondary pressure P2 is all cancelled, and the above equation can be further sorted into p1×s2=f1+f2. The pressure adjustment valve 100a of the present embodiment is configured such that the effective pressure receiving area S1 of the pressure-sensitive bellows 51 and the pressure receiving area S2 of the valve portion 42 surrounded by the valve seat 18 match, and therefore the influence of the secondary side pressure P2 can be canceled. That is, the pressure regulating valve 100a can variably control the opening degree according to the variation of the primary side pressure by appropriately setting the biasing force F2 of the regulating spring 63 by moving the regulating spring member 62 in the axial direction. The size of each portion of the pressure control valve 100a may be set using an actual pressure receiving area obtained by experiment, not only the pressure receiving area (effective pressure receiving area) calculated as an approximate value based on the average inner diameter of the minimum inner diameter and the maximum inner diameter of the bellows shape.
(case where the primary side pressure P1 is higher than the set value)
When the primary pressure P1 is higher than the set value ((f1+f2)/S2) (for example, a state where the discharge pressure of the compressor is increased, etc.), the valve portion 42 is separated from the valve seat 18, which is not shown, and is in a valve-opened state. At this time, the valve opening increases with the rise of the primary pressure P1, but the maximum valve opening is defined by the abutment of the stepped portion 54c of the connecting rod 54 and the bellows upper cover engagement portion 53b of the bellows upper cover 53, and the connecting member 83b is held so as not to fall off from the sliding portion 53 c.
The first upper connection mechanism 80a of the present embodiment can suppress the inclination of the connecting rod 54 with respect to the central axis C, and can be in a point contact state and a non-contact state with respect to the sliding portion 53C and the insertion hole 53a, respectively. This eliminates the conventional problem (increase in sliding resistance) and reduces the hysteresis, so that even when the pressure at which the valve starts to open (primary side pressure P1 is slightly smaller than the set value ((f1+f2)/S2)), it is possible to ensure low valve leakage.
(second embodiment)
The pressure regulating valve 100b according to the second embodiment of the present invention will be described with reference to fig. 4. The pressure adjustment valve 100b of the second embodiment is different from the pressure adjustment valve 100a of the first embodiment in that the shape of the lower engaging portion 81 is changed from a conical shape to a spherical shape, and other basic configurations are the same as those of the first embodiment. Here, the same components are denoted by the same reference numerals, and repetitive description thereof will be omitted.
First, in the first embodiment, as shown in fig. 3 (a), the urging force of the adjustment spring 63 is transmitted through an annular contact line formed by the contact between the lower engaging portion 81c and the connecting member 83b. Here, a centripetal action is applied between the lower engaging portion 81C and the connecting member 83b, but a state in which the center position of the lower engaging portion 81C temporarily deviates from the center axis C in the radial direction, that is, a transitional state may occur. In this transitional state, since the axial direction passing through the annular contact line is at an angle to the central axis C, the force not transmitted along the central axis C is transmitted to the needle 40, and as a result, there is a concern that the valve leakage of the needle 40 is reduced.
The second upper connecting mechanism 80b of the second embodiment is configured by a spherical lower engaging portion 81s having a center on the center axis C, a conical upper engaging portion 82C, and a spherical connecting member 83b. Here, the radius Rc of the spherical shape of the lower engaging portion 81s is set to be larger than the radius Ra of the connecting member 83b (Rc > Ra). Thus, the spherical lower engaging portion 81s and the spherical connecting member 83b are always in a point contact state, and the edge portion of the spherical lower engaging portion 81s can be prevented from abutting the spherical connecting member 83b.
In this way, in the second upper connection mechanism 80b, even in a transitional state in which the center position of the lower engaging portion 81s temporarily deviates from the center axis C in the radial direction, the lower engaging portion 81s and the connection member 83b always face each other in the substantially center axis C direction and are in point contact with each other. As a result, the second upper connection mechanism 80b can transmit the biasing force of the adjustment spring 63 to the needle 40 in the direction along the central axis C, and as a result, the valve leakage performance of the needle 40 can be improved.
As described above, in the second embodiment, in addition to the same effect (reduction of hysteresis) as in the first embodiment, the second upper connection mechanism 80b always transmits the force in the direction along the central axis C, whereby the valve leakage of the needle 40 can be improved.
(third embodiment)
A pressure regulating valve 100c according to a third embodiment of the present invention will be described with reference to fig. 5. The pressure regulating valve 100c of the third embodiment is different from the pressure regulating valve 100a of the first embodiment in that the shape of the connecting member 83 is changed from a spherical shape to a mushroom shape, and other basic structures are the same as those of the first embodiment. Here, the same components are denoted by the same reference numerals, and repetitive description thereof will be omitted.
The third upper connecting mechanism 80C of the third embodiment is configured by a conical lower engaging portion 81C having a center on the center axis C, a conical upper engaging portion 82C, and a mushroom-shaped connecting member 83 m. Here, the upper portion 83mu, the side portion 83ms, and the lower portion 83md of the connecting member 83m have spherical shapes, respectively, and are always in contact with the upper engaging portion 82c, the sliding portion 53c, and the lower engaging portion 81 c.
As described above, the connecting member 83 of the present embodiment does not need to have a spherical shape as in the connecting member 83b of the first embodiment, and can have a mushroom shape as in the connecting member 83m, so that the degree of freedom in design can be improved.
Specifically, as shown in fig. 5, when the apex angles of the conical shapes of the upper engaging portion 82c and the lower engaging portion 81c are set to different angles, the radii of the spherical shapes of the upper portion 83mu and the lower portion 83md of the connecting member 83m can be set to appropriate values, respectively. This can more effectively act on the centripetal force generated between the conical upper engaging portion 82c and the conical lower engaging portion 81c and the connecting member 83 m. Further, by setting the radii of the spherical shapes of the lower portion 83md, the upper portion 83mu, and the side portion 83ms of the connecting member 83m to appropriate values, the connecting member 83m can be prevented from abutting the annular edges of the lower engaging portion 81c and the upper engaging portion 82c, and the connecting member 83m can be brought into a point contact state with the sliding portion 53 c.
In the present embodiment, the lower portion 83md of the connecting member 83m has a shape protruding toward one end, and the lower engaging portion 81c has a shape recessed toward one end, but the present invention is not limited thereto. For example, the lower portion 83md of the connecting member 83m may be recessed toward the other end, and the lower engaging portion 81c may be projected toward the other end. In the present embodiment, the lower portion 83md of the connecting member 83m has a spherical shape, while the lower engaging portion 81c has a conical shape, but the present invention is not limited thereto. For example, the lower portion 83md and the lower engaging portion 81c of the connecting member 83m may each have a spherical shape, or the lower portion 83md and the lower engaging portion 81c of the connecting member 83m may each have a conical shape.
As described above, in the third embodiment, in addition to the same effects (reduction of hysteresis) as in the first embodiment, the degree of freedom in design of the connection member 83m of the third upper connection mechanism 80c can be improved.
(fourth embodiment)
A pressure regulating valve 100d according to a fourth embodiment of the present invention will be described with reference to fig. 6. The pressure adjustment valve 100d of the fourth embodiment can be employed in a case where the outer diameter of the adjustment spring 63 is small, and is different from the pressure adjustment valve 100a of the first embodiment in that the spring seat member 61 and the connecting member 83b are integrated, and other basic structures are the same as those of the first embodiment. Here, the same components are denoted by the same reference numerals, and repetitive description thereof will be omitted.
The fourth upper connecting mechanism 80d of the fourth embodiment is composed of a conical lower engaging portion 81c and a spring seat connecting member (connecting mechanism) 84 s. Here, the spring seat connecting member 84s includes a flange portion 84sf, and the flange portion 84sf extends in the radial direction and directly abuts against one end side of the adjustment spring 63. The side portion 84ss and the lower portion 84sd of the spring seat connecting member 84s have spherical shapes, respectively, and are always in contact with the sliding portion 53c and the lower engaging portion 81 c. Further, the adjustment spring 63 is held by the flange 84sf so that movement in the radial direction is restricted, and can be inserted into the slide portion 53c in a non-contact state.
In this way, when the outer diameter of the adjustment spring 63 is small, the spring seat member 61 and the connecting member 83b are integrated in the fourth upper connecting mechanism 80d, so that the number of parts can be reduced, and thus the burden on the assembly work and the parts management can be reduced.
In the present embodiment, the lower portion 84sd of the spring seat connecting member 84s has a shape protruding toward one end, and the lower engaging portion 81c has a shape recessed toward one end. For example, the lower portion 84sd of the spring seat connecting member 84s may be recessed toward the other end, and the lower engaging portion 81c may be projected toward the other end.
As described above, in the fourth embodiment, in addition to the same effects (reduction of hysteresis) as in the first embodiment, the fourth upper connection mechanism 80d can reduce the burden on the assembly work and the parts management.
(fifth embodiment)
A pressure regulating valve 100e according to a fifth embodiment of the present invention will be described with reference to fig. 7. The pressure adjustment valve 100e of the fifth embodiment is different from the pressure adjustment valve 100d of the fourth embodiment in that the shape of the lower engaging portion 81 is changed from a conical shape to a spherical shape, and other basic configurations are the same as those of the fourth embodiment. Here, the same components are denoted by the same reference numerals, and repetitive description thereof will be omitted.
The fifth upper connecting mechanism 80e of the fifth embodiment is configured by a lower engaging portion 81s having a spherical shape centered on the center axis C and a spring seat connecting member 84 s. The spherical lower engaging portion 81s is the same as that of the second embodiment.
In the fifth upper connecting mechanism 80e, as in the second embodiment, even in a transitional state in which the center position of the lower engaging portion 81s temporarily deviates from the center axis C in the radial direction, the lower engaging portion 81s and the lower portion 84sd of the spring seat connecting member 84s always face each other in the substantially center axis C direction and are in point contact with each other. As a result, the fifth upper connection mechanism 80e can transmit the biasing force of the adjustment spring 63 to the needle 40 in the direction along the central axis C, and as a result, the valve leakage of the needle 40 can be improved.
In the present embodiment, the lower portion 84sd of the spring seat connecting member 84s is formed in a shape protruding toward one end, and the lower engaging portion 81s is formed in a shape recessed toward one end. For example, the lower portion 84sd of the spring seat connecting member 84s may be recessed toward the other end, and the lower engaging portion 81s may be projected toward the other end.
As described above, in the fifth embodiment, in addition to the same effects as those of the first and fourth embodiments (reduction of hysteresis, reduction of load on assembly work and the like), the same effects as those of the second embodiment (improvement of valve leakage of the needle) can be obtained.
(sixth embodiment)
A pressure regulating valve 100f according to a sixth embodiment of the present invention will be described with reference to fig. 8. The pressure adjustment valve 100f of the sixth embodiment is different from the pressure adjustment valve 100d of the fourth embodiment in that the shape of the lower portion of the spring seat connecting member 84s is changed from a spherical shape to a conical shape, and other basic configurations are the same as those of the fourth embodiment. Here, the same components are denoted by the same reference numerals, and repetitive description thereof will be omitted.
The sixth upper connecting mechanism 80f of the sixth embodiment is composed of a conical lower engaging portion 81c and a conical spring seat connecting member 84c provided at the lower portion 84 cd. Here, the apex angle of the conical shape of the lower engaging portion 81c is set to be larger than the apex angle of the conical shape of the lower portion 84cd of the spring seat connecting member 84c, and the lower engaging portion 81c and the spring seat connecting member 84c are always in a point contact state. As a result, the lower portion 84cd of the spring seat connecting member 84C, which is restrained from moving in the radial direction, acts centripetally toward the lower engaging portion 81C, and therefore the center position of the conical lower engaging portion 81C is autonomously disposed in the vicinity of the central axis C.
Here, when the apex angle of the conical shape of the lower engaging portion 81c is made close to the apex angle of the conical shape of the lower portion 84cd of the spring seat connecting member 84c, the centripetal action acting on the spring seat connecting member 84c and the lower engaging portion 81c can be more effectively exerted. On the other hand, when the apex angle of the conical shape of the lower engaging portion 81C is increased, even in a transitional state in which the center position of the lower engaging portion 81C temporarily deviates from the center axis C in the radial direction, the lower engaging portion 81C and the lower portion 84cd of the spring seat connecting member 84C always face each other in the substantially center axis C direction and are in point contact with each other. As a result, the sixth upper connection mechanism 80f can transmit the biasing force of the adjustment spring 63 to the needle 40 in the direction along the central axis C, and as a result, the valve leakage of the needle 40 can be improved. The apex angle of the conical shape of the lower engaging portion 81c is less than 180 (°), preferably 100 (°) to 170 (°).
In the present embodiment, the lower portion 84cd of the spring seat connecting member 84c has a shape protruding toward one end, and the lower engaging portion 81s has a shape recessed toward one end, but the present invention is not limited thereto. For example, the lower portion 84sd of the spring seat connecting member 84s may be recessed toward the other end, and the lower engaging portion 81s may be projected toward the other end.
As described above, in the sixth embodiment, in addition to the same effects (reduction of hysteresis, reduction of load on assembly work, etc.) as in the first and fourth embodiments, the sixth upper connection mechanism 80f can also more effectively exert a centripetal action, and by transmitting the force in the direction along the central axis C at all times, the valve leakage of the needle 40 can be improved.
< others >
It is to be noted that the pressure adjustment valves 100a to 100f according to the present embodiment can be applied not only to the illustrated refrigerant circuit but also to all fluid devices and fluid circuits. The present invention is not limited to the above-described embodiments, and modifications described here and there, and can be appropriately changed or modified without departing from the scope of the technical idea of the present invention.
Claims (8)
1. A pressure regulating valve is characterized by comprising:
a valve body having a valve seat;
a needle having a valve portion that can be moved toward and away from the valve seat;
a pressure-sensitive bellows unit having a pressure-sensitive bellows that expands and contracts in an axial direction;
an adjustment spring unit having an adjustment spring for biasing the valve portion in a valve closing direction; and
a connection mechanism for connecting the pressure-sensitive bellows unit and the adjustment spring unit,
The pressure-sensitive bellows unit includes: a bellows cover on the side of the adjustment spring unit, which has an insertion hole and a sliding portion that communicate in the axial direction and is fixed so as not to be relatively displaced with respect to the valve main body, or is integrally formed with the valve main body; a bellows cover on the needle side; the pressure-sensitive bellows is fixed so that the needle-side end is connected to the needle-side bellows cap and the adjustment spring unit-side end is connected to the adjustment spring unit-side bellows cap so as to be not relatively displaced with respect to the valve main body; and a connecting rod configured such that the end on the needle side is connected to the bellows cover on the needle side, and the end on the adjusting spring unit side is capable of being inserted into the insertion hole and the sliding portion,
the above-mentioned coupling mechanism includes: an engaging portion provided at an axial center portion of the end portion of the connecting rod on the side of the adjustment spring unit; and a connecting member having a spherical shape on a side portion thereof and being in point contact with the sliding portion,
the end of the connecting member on the needle side and the engaging member have one and the other of a concave shape and a convex shape along the axial direction, respectively, to form concave-convex engaging with centripetal action,
The first gap formed between the connecting rod and the insertion hole is made larger than the second gap formed between the connecting member and the sliding portion.
2. The pressure regulating valve of claim 1, wherein,
the third gap formed between the connecting rod and the valley portion of the pressure-sensitive bellows is made larger than the gap obtained by adding the fourth gap formed by the connection between the end portion of the connecting rod on the needle side and the bellows cover on the needle side to the second gap.
3. The pressure regulating valve according to claim 1 or 2, wherein,
the side portion of the connecting member that is in point contact with the sliding portion is the outermost diameter portion of the connecting member when viewed in the axial direction.
4. The pressure regulating valve according to claim 1 or 2, wherein,
the length of a sliding region from a point contact position of the sliding portion and a side portion of the connecting member to an end portion of the sliding portion on the side of the adjustment spring unit in a valve-closed state of the pressure adjustment valve is set to be larger than the maximum lift amount of the needle.
5. The pressure regulating valve according to claim 1 or 2, wherein,
The needle-side end of the adjustment spring is directly abutted against the connecting member, and the adjustment spring is inserted into the sliding portion in a non-contact state.
6. The pressure regulating valve according to claim 1 or 2, wherein,
the shape of the engagement portion is a conical shape, and the shape of the needle-side end of the connecting member is a spherical shape,
the vertex angle θ of the conical shape of the engagement portion satisfies θ > 180-2×sin, which is a radius Ra of the spherical shape of the needle-side end portion of the connecting member and a radius Rb of the conical bottom surface of the engagement portion -1 (Rb/Ra)。
7. The pressure regulating valve according to claim 1 or 2, wherein,
the shape of the engaging portion and the shape of the needle-side end of the connecting member are spherical,
the radius of the spherical shape of the engagement portion is made larger than the radius of the spherical shape of the needle-side end portion of the connecting member.
8. The pressure regulating valve according to claim 1 or 2, wherein,
the shape of the engaging portion and the shape of the needle-side end of the connecting member are tapered,
the apex angle of the conical shape of the engagement portion is made larger than the apex angle of the conical shape of the needle-side end portion of the connecting member.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2020211294A JP7376464B2 (en) | 2020-12-21 | 2020-12-21 | pressure regulating valve |
| JP2020-211294 | 2020-12-21 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114645961A CN114645961A (en) | 2022-06-21 |
| CN114645961B true CN114645961B (en) | 2023-11-07 |
Family
ID=81991810
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111478611.3A Active CN114645961B (en) | 2020-12-21 | 2021-12-06 | pressure regulating valve |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP7376464B2 (en) |
| CN (1) | CN114645961B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1039880A (en) * | 1988-06-10 | 1990-02-21 | 三菱重工业株式会社 | The energy force control valve of compressor |
| JP2005147363A (en) * | 2003-11-19 | 2005-06-09 | Time Engineering Co Ltd | Flow control valve |
| CN202580183U (en) * | 2012-01-05 | 2012-12-05 | 株式会社鹭宫制作所 | Pressure adjustment valve |
| CN104251325A (en) * | 2013-06-28 | 2014-12-31 | 株式会社鹭宫制作所 | Pressure operating valve and pressure setting method of pressure operating valve |
| CN106979337A (en) * | 2015-10-12 | 2017-07-25 | 艾默生过程管理调节技术公司 | Control member for fluid control devices |
| CN107615204A (en) * | 2015-06-09 | 2018-01-19 | 株式会社电装 | Pressure-reducing valve |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013024135A (en) | 2011-07-21 | 2013-02-04 | Saginomiya Seisakusho Inc | Pressure-sensitive control valve |
| JP2013087863A (en) | 2011-10-18 | 2013-05-13 | Saginomiya Seisakusho Inc | Pressure sensitive control valve |
| JP6042631B2 (en) | 2012-04-27 | 2016-12-14 | 株式会社テイエルブイ | Pressure reducing valve |
| CN109667967A (en) | 2018-12-28 | 2019-04-23 | 捷锐企业(上海)有限公司 | Bellows diaphragm type high-cleanness high-pressure pressure-reducing valve |
| CN210087999U (en) | 2019-01-23 | 2020-02-18 | 永嘉县瑞隆阀门有限公司 | Double-balance type corrugated pipe pressure reducing valve |
-
2020
- 2020-12-21 JP JP2020211294A patent/JP7376464B2/en active Active
-
2021
- 2021-12-06 CN CN202111478611.3A patent/CN114645961B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1039880A (en) * | 1988-06-10 | 1990-02-21 | 三菱重工业株式会社 | The energy force control valve of compressor |
| JP2005147363A (en) * | 2003-11-19 | 2005-06-09 | Time Engineering Co Ltd | Flow control valve |
| CN202580183U (en) * | 2012-01-05 | 2012-12-05 | 株式会社鹭宫制作所 | Pressure adjustment valve |
| CN104251325A (en) * | 2013-06-28 | 2014-12-31 | 株式会社鹭宫制作所 | Pressure operating valve and pressure setting method of pressure operating valve |
| CN107615204A (en) * | 2015-06-09 | 2018-01-19 | 株式会社电装 | Pressure-reducing valve |
| CN106979337A (en) * | 2015-10-12 | 2017-07-25 | 艾默生过程管理调节技术公司 | Control member for fluid control devices |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114645961A (en) | 2022-06-21 |
| JP2022097991A (en) | 2022-07-01 |
| JP7376464B2 (en) | 2023-11-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8708309B2 (en) | Self-aligning spring seat for fluid regulator and fluid regulator comprising self-aligning spring seat | |
| RU2315348C2 (en) | Fluid pressure regulator | |
| US6622752B2 (en) | Pressure relief valve | |
| US8939167B2 (en) | Adjustable fixed pressure relief assembly and regulator comprising same | |
| JP5453227B2 (en) | Pressure reducing valve | |
| US20120234407A1 (en) | Pressure regulator | |
| EP0187769B1 (en) | In-line check valve having combined downstream poppet support and flow control elements | |
| CN114645961B (en) | pressure regulating valve | |
| EP1811356A1 (en) | Pressure-reducing valve | |
| JP2007100769A (en) | Pressure regulating device | |
| US10817002B2 (en) | Gas valve and gas control device | |
| JP2002005319A (en) | Pressure relief valve | |
| CN115013575A (en) | Pressure regulating valve | |
| WO2012137424A1 (en) | Pressure reduction valve | |
| JP7431118B2 (en) | pressure regulating valve | |
| US20110048553A1 (en) | Pressure regulator | |
| WO2015052863A1 (en) | Pressure reducing valve | |
| CN116733654A (en) | Fuel pump for direct injection system | |
| US20240019038A1 (en) | Pressure reduction valve | |
| CN116733653A (en) | Fuel pump for direct injection system | |
| JP7461195B2 (en) | pressure regulating valve | |
| US11808363B1 (en) | Resilient metal seal for check valve | |
| JP2023163426A (en) | Pressure regulation valve | |
| US20240053778A1 (en) | A gas-pressure regulator | |
| CN102135202A (en) | Valve body for opening and closing flow path |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |