WO2021218050A1 - 阀组件及压缩机 - Google Patents

阀组件及压缩机 Download PDF

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Publication number
WO2021218050A1
WO2021218050A1 PCT/CN2020/121412 CN2020121412W WO2021218050A1 WO 2021218050 A1 WO2021218050 A1 WO 2021218050A1 CN 2020121412 W CN2020121412 W CN 2020121412W WO 2021218050 A1 WO2021218050 A1 WO 2021218050A1
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WO
WIPO (PCT)
Prior art keywords
valve
fastening
valve assembly
valve plate
mounting hole
Prior art date
Application number
PCT/CN2020/121412
Other languages
English (en)
French (fr)
Inventor
马宏伟
朱小莉
杨涛
Original Assignee
艾默生环境优化技术(苏州)有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN202010365060.9A external-priority patent/CN113586772A/zh
Priority claimed from CN202020713317.0U external-priority patent/CN212536796U/zh
Application filed by 艾默生环境优化技术(苏州)有限公司 filed Critical 艾默生环境优化技术(苏州)有限公司
Publication of WO2021218050A1 publication Critical patent/WO2021218050A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • 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
    • F16K15/00—Check valves
    • F16K15/14—Check valves with flexible valve members

Definitions

  • the present disclosure relates to a valve assembly and a compressor including the valve assembly.
  • a one-way valve is usually installed at the exhaust port of the scroll assembly of the compressor to prevent the high temperature and high pressure refrigerant gas from back-filling the inside of the scroll assembly , which in turn leads to repeated compression of the refrigerant gas.
  • a one-way valve usually includes a valve stop and a valve plate arranged below the valve stop, wherein the valve plate can open or close the fluid through hole under the action of fluid pressure, and the valve stop can be used to limit the displacement range of the valve plate.
  • An object of one or more embodiments of the present disclosure is to provide a valve assembly that reduces or eliminates valve plate wear to have high reliability.
  • a valve assembly that is mounted to a fixed part provided with a fluid through hole
  • the valve assembly includes: a valve disc configured to be positioned to open the An open position of the fluid through hole and a closed position of the fluid through hole, and the valve plate is formed with a first mounting hole; a valve stop, the valve stop including a holding portion and configured to limit the displacement range of the valve plate
  • the retaining portion has a flat surface that abuts against the valve plate, the retaining portion has an inclined surface extending away from the valve plate from the retaining portion, and the valve stop is formed with a first Two mounting holes; and a mounting member configured to mount the valve disc and the valve stop to the fixing member, the mounting member including extending through the first mounting hole and the second
  • the mounting hole extends to the connecting portion of the fixed component and the fastening portion provided against the valve stop, characterized in that it extends from the boundary line of the retaining portion and the limiting portion to the second mounting hole The first distance from the central surface of the fast
  • the fastening portion includes a fastening head and a fastening washer, wherein the fastening head applies a fastening force to the valve stop and the valve plate, and the fastening The gasket is clamped between the fastening head and the valve stop.
  • the end portion of the portion of the fastening gasket that is in contact with the valve stopper farthest from the center surface serves as the effective fastening end portion.
  • the valve plate includes a first valve plate and a second valve plate arranged adjacently, and the first valve plate is disposed between the valve stop and the second valve plate, so The second valve plate is arranged between the first valve plate and the fixing member.
  • the holding part is provided with a recess for accommodating the fastening part.
  • the limiting portion extends from the holding portion in a first direction, and the holding portion is symmetrically arranged with respect to the second mounting hole in a second direction perpendicular to the first direction
  • the inclined surface of the limiting portion is formed as an arc-shaped inclined surface.
  • the ratio of the first distance to the second distance is less than 1.3.
  • a compressor including the valve assembly described above.
  • the compressor is a scroll compressor
  • the scroll compressor includes a compression mechanism adapted to compress a working fluid, and an internal space of the scroll compressor to separate a non-high pressure area And the muffler cover of the low pressure area, and the fixing member is installed at the through hole of the muffler cover or the exhaust port of the scroll compressor, and the fluid through hole is connected to the central compression chamber of the compression mechanism. Connected.
  • Fig. 1 is a cross-sectional view schematically showing a scroll compressor to which a valve assembly according to a comparative example is applied;
  • FIGS. 2 and 3 are perspective views schematically showing a valve assembly according to a comparative example
  • FIG. 4 is a cross-sectional view schematically showing the valve assembly according to the first embodiment of the present disclosure
  • FIGS. 5a and 5b are schematic diagrams showing the wear analysis of the valve assembly according to the comparative example and the valve assembly according to the first embodiment of the present disclosure
  • FIG. 6 is a cross-sectional view schematically showing the valve assembly according to the first embodiment of the present disclosure.
  • FIG. 7 is a cross-sectional view schematically showing an alternative embodiment of the mounting member of the valve assembly according to the present disclosure.
  • the compressor 1 includes a substantially closed casing 20.
  • the housing 20 may be composed of a substantially cylindrical body part 22, a top cover 24 provided at one end of the body part 22, and a bottom cover 26 provided at the other end of the body part 22.
  • a partition 30 is provided between the top cover 24 and the body portion 22 to partition the internal space of the housing 20 into a low-pressure fluid suction chamber 21 and a high-pressure fluid discharge chamber 23.
  • the space between the partition 30 and the top cover 24 constitutes a fluid discharge chamber 23, and the space between the partition 30, the body portion 22 and the bottom cover constitutes a fluid suction chamber 21.
  • An air inlet connector for sucking fluid is provided on one side of the fluid suction chamber 21, and an exhaust connector for discharging compressed fluid is provided on one side of the fluid discharge chamber 23.
  • the housing 20 is provided with a compression mechanism and a driving mechanism for driving the compression mechanism.
  • the compression mechanism sucks fluid from the fluid suction chamber 21 of the housing 20 and compresses the fluid and discharges the fluid into the fluid discharge chamber 23 of the housing 20.
  • the compression mechanism may include a fixed scroll 40 and a movable scroll 50, for example.
  • the movable scroll 50 includes an end plate 54 and a spiral scroll 56 formed on one side of the end plate.
  • the fixed scroll 40 includes an end plate 44 and a spiral wrap 46 formed on one side of the end plate.
  • the end plate 44 includes an exhaust port 42 formed at a substantially central position of the end plate.
  • the scroll 46 of the fixed scroll 40 and the scroll 56 of the movable scroll 50 mesh with each other and form a series of compression chambers whose volumes gradually decrease from the radially outer side to the radially inner side to compress the fluid.
  • the compressed fluid is sucked in through the radially outermost compression chamber, and the compressed fluid is discharged through the radially innermost compression chamber.
  • the working fluid compressed by the fixed scroll 40 and the movable scroll 50 flows toward the high-pressure fluid discharge chamber 23 through the exhaust port 42 and the through hole of the partition (silence cover) 30, in order to prevent the high-pressure side
  • the working fluid flows back into the compression mechanism, for example, at the through hole of the muffler cover 30 or adjacent to the exhaust port of the compression mechanism (see FIG. 1, on the upper side of the end plate 44 of the fixed scroll 40 by the fixed scroll
  • a valve assembly 100 is provided in the exhaust space defined by the hub of the spin 40).
  • the valve assembly 100 is configured to allow the working fluid in the compression chamber of the compression mechanism to flow to the high pressure side, but prevent the working fluid on the high pressure side from flowing back into the compression chamber.
  • the valve assembly 100 may include a valve disc 110, a valve stop 120 and a mounting member 130.
  • the valve plate 110 may include a first valve plate 110a and a second valve plate 110b arranged up and down, wherein the first valve plate 110a may be disposed between the valve stop 120 and the second valve plate 110b and the second valve plate 110b may be disposed on Between the first valve disc 110a and the valve assembly fixing seat 60.
  • each valve plate is formed with a fixed portion 112 and a movable portion 114, and the movable portion 114 is configured to be movable relative to the fixed portion 112 to selectively open or close the fluid passage hole provided at the fixed seat 60 ,
  • the fixing portion 112 may have a first mounting hole 116.
  • a valve stop 120 is provided above the valve plate 110 to limit the displacement range of the valve plate 110.
  • the valve stop 120 includes a retaining portion 122 and a limiting portion 124 extending from the retaining portion 122 in the longitudinal direction (also referred to as a first direction), wherein the retaining portion 122 has a flat surface against the valve plate and the retaining portion 122 has a second mounting
  • the hole 126 and the limiting portion 124 have an inclined surface extending away from the valve plate 110 from the retaining portion.
  • the mounting member 130 is used for mounting the valve plate 110 and the valve stop 120 to the fixing seat 60, and the mounting member 130 may include a connecting portion 132 and a fastening portion 134.
  • the connecting portion 132 may extend through the first mounting hole 116 and the second mounting hole 126 and be fixed to the fixing seat 60.
  • the fastening portion 134 includes a fastening head 136 that applies a fastening force to the valve stop 120 and the valve plate 110 and a fastening pad 138 clamped between the fastening head 136 and the valve plate 120.
  • the mounting member 130 is exemplarily shown as including a bolt and a fastening washer 138, where the bolt includes a connecting portion 132 and a fastening head 136.
  • the holding portion 122 may be provided with a recess for accommodating the fastening portion 134 to save installation space of the valve assembly, and the holding portion 122 is symmetrically about the second installation hole 126 in a transverse direction (also called a second direction) perpendicular to the longitudinal direction. Two pins are provided, and the pins pass through the pin holes formed on the valve plate to prevent the valve plate from laterally shifting (for example, lateral shifting due to rotation).
  • the working fluid is sucked into the compression mechanism and compressed as it flows from the radially outermost position to the radially innermost position, and the compressed fluid is discharged through the fluid through hole.
  • the pressure on the lower side of the valve plate 110 is greater than the pressure on the upper side, and the valve plate 110 moves toward the open position under the action of the pressure difference, thereby allowing the fluid to pass through the fluid.
  • Through hole discharge When the pressure of the fluid contained in the central compression chamber is less than the pressure of the fluid in the discharge chamber 23, the valve plate 110 returns to the closed position under the action of the elastic restoring force and the pressure difference.
  • valve plate 110 when the valve assembly 100 according to the comparative example is in use, the valve plate 110 is prone to wear. In the case of severe wear, the valve plate 110 may even be broken, thereby causing the fluid in fluid communication with the central compression chamber to be broken.
  • the through hole is always connected to the high-pressure side. In this case, the compressed working fluid will flow back into the compression chamber from the high-pressure side, causing the compressor to repeatedly compress the working fluid, which will obviously adversely affect the compression efficiency.
  • the present disclosure proposes an improved valve assembly, which can effectively solve the wear problem of the valve plate, thereby avoiding the performance of the compressor due to the wear failure of the valve assembly.
  • valve assembly according to the present disclosure and the compressor applying the valve assembly will be described in further detail with reference to FIGS. 4 to 7.
  • Fig. 4 schematically shows a cross-sectional view of the valve assembly according to the first embodiment of the present disclosure.
  • the valve assembly 200 may be mounted to the fixing seat 60 (corresponding to the fixing part according to the present disclosure) and may include a valve plate 110, a valve stopper having a second mounting hole 226 220 and mounting parts 130.
  • the structure and function of the valve disc and the mounting member of the valve assembly 200 according to the exemplary embodiment of the present disclosure are the same as the corresponding parts of the valve assembly 100 according to the comparative example, and will not be repeated here.
  • the valve stop 220 of the valve assembly 200 is configured similarly to the valve stop 120 of the valve assembly 100 according to the comparative example to limit the displacement range of the valve plate 110 and includes a holding portion 222 and a limiting portion 224, The difference is that, compared with the holding portion 122 of the valve stop 120, the holding portion 222 of the valve stop 220 has an increased length.
  • FIGS. 5a and 5b it will be described in detail with reference to FIGS. 5a and 5b.
  • the inventor of the present disclosure found that when the compressor is operating, the upper and lower valve plates 110a and 110b of the valve plate 110 reciprocate in the open position and the closed position.
  • the two valve plates cannot be opened and closed completely synchronously, which will inevitably be in the movable part of the two valve plates. There is a slight relative displacement between them.
  • the straight line L extends through the boundary line between the stop portion 124 and the holding portion 122 (shown as the intersection point O in FIG.
  • the distance B from the end E to the central axis C of the second mounting hole is equal to the distance A from the intersection O between the stop portion 124 and the holding portion 122 to the central axis C,
  • the point of action of the tightening force on the valve plate 110 is exactly on the straight line L and coincides with the intersection point F1. That is to say, at the intersection point F1, on the one hand, the valve plates 110a and 110b are subjected to the downward positive pressure exerted by the fastening portion 134, and on the other hand, there is a relative displacement of the valve plates 110a and 110b, which will cause the valve plates to occur.
  • the boundary line between the limit part and the holding part refers to the boundary line between the limit part and the holding part of the valve stop. This boundary line is shown as a point of intersection O in the cross-sectional view.
  • the inventor according to the present disclosure cleverly conceived the valve assembly 200 having the elongated holding portion 222.
  • the distance A from the intersection O between the limiting portion 224 and the holding portion 222 to the central axis C (the first distance) is greater than The distance (second distance) B from the end (effectively fastened end) E of the fastening portion 134 to the central axis C.
  • the fastening portion 134 applies a fastening force to the valve stop 220 and the valve disc 110, the point of action of the fastening force on the valve disc 110 is aligned with the position of the end E and is shifted from the straight line L.
  • the distance A may be in the range of 1 to 1.3 times the distance B (not including the end value). According to experiments, the inventor found that the ratio of the distance A to the distance B can effectively reduce and avoid fretting wear, and is beneficial to minimize the modification of the valve assembly, thereby facilitating manufacturing and saving costs.
  • the applicant further found that when the distance A is in the range of 1.05 to 1.1 times the distance B, the effects in all aspects are more prominent.
  • the end E is also referred to as the effective fastening end of the fastening part.
  • the effective fastening end portion refers to the side end of the fastening portion close to the limiting portion, and when the fastening portion is arranged irregularly (for example, the fastening portion is formed as a polygon with a plurality of ends) Structure), then the fastening end refers to the end that passes through the central axis C and is parallel to the central plane of the boundary line O, which is the farthest end, in particular, when the fastening portion is along the vertical direction
  • the effective fastening end refers to the part where the fastening part is in contact with the valve stop (that is, the lower side is narrower).
  • the fastening portion includes both the fastening head and the fastening gasket as shown in FIG. 4, the end of the portion where the fastening gasket contacts the valve stopper farthest from the center surface serves as the effective fastening end.
  • FIG. 6 shows a cross-sectional view of the valve assembly 300 according to the second embodiment of the present disclosure.
  • the valve assembly 300 may include a valve plate 110, a valve stop 120 and a mounting member 330.
  • the structure and function of the valve disc and valve stop of the valve assembly 300 according to the second embodiment of the present disclosure are the same as the corresponding parts of the valve assembly 100 according to the comparative example, and will not be repeated here.
  • the mounting member 330 of the valve assembly 300 according to the second embodiment of the present disclosure and the mounting member 130 of the valve assembly 100 according to the comparative example similarly include a connecting part 332 and a fastening part 334, wherein the connecting part 332 may extend through Passing through the first mounting hole and the second mounting hole and being fixed to the fixing seat 60, and the fastening portion 334 includes a fastening head 336 for applying fastening force to the valve stop 120 and the valve plate 110, and a fastening head 336 that is clamped on the fastening head 336.
  • the fastening gasket 338 between the valve stop 120 and the mounting part 330 is different from the mounting part 130 in that the fastening gasket 338 has a reduced radius compared with the fastening gasket 138.
  • the distance A from the intersection O to the central axis C is greater than from the end E of the fastening washer 338 to the center
  • the distance B of the axis C (in this embodiment, the end E of the fastening washer 338 serves as an effective fastening end according to the present disclosure).
  • the mounting member is exemplarily shown as including a bolt and a fastening washer, wherein the bolt includes a connecting portion and a fastening head, but The present disclosure is not limited to this, and the mounting member 130' may also include rivets and fastening gaskets (as shown in FIG. 7).
  • the standard valve stop and the standard mounting parts can be used directly without modification.
  • standard bolts and standard bolts with smaller sizes can be used. Matching smaller standard gaskets. In this way, a valve assembly with high reliability can be provided in a convenient and cost-effective manner.
  • valve assembly 300 is exemplarily described according to the second embodiment of the present disclosure as having a tightening gasket 338 with a reduced radius, those skilled in the art should understand that the valve assembly may also have a tightening head with a reduced radius. Since the radius of the fastening head 336 is reduced, the distance A from the intersection O to the central axis C is greater than the distance B from the end of the fastening head 336 to the central axis C (in this modification, the fastening The end of the head serves as an effective fastening end according to the present disclosure).
  • the mounting member is shown as including a fastening gasket, the present disclosure is not limited to this, and the fastening gasket may be omitted and only the fastening head and the connecting portion may be used. Installation parts.
  • valve plate 110 includes two valve plates 110a and 110b, but the present disclosure is not limited thereto, and the valve plate 110 may also be formed as a single valve plate.
  • the valve plate 110 is a single valve plate, since the valve plate 110 has a relative displacement between the valve plate 110 and the upper valve position during the opening and closing process of the valve plate 110, fretting wear of the valve plate 110 may also occur.
  • fretting wear of the valve plate 110 may also occur.
  • the use of the valve assembly according to the exemplary embodiment of the present disclosure can also solve the wear problem of such a single valve plate.
  • the valve assembly 200 may preferably include two valve plates 110a and 110b.
  • valve plate even if one valve plate is damaged or broken, the other valve plate can still be used to selectively open or close the fluid through hole. Therefore, the risk of failure of the valve assembly can be further reduced, and the working fluid can be prevented from returning to the compression chamber, thereby ensuring the working efficiency of the compressor.
  • valve assembly can also be applied to other compressors besides the scroll compressor and can also be applied to any other machinery requiring a one-way valve besides the compressor. All these modifications and variations fall within the scope of the present disclosure. Moreover, all the components described herein can be replaced by other technically equivalent components.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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  • Compressor (AREA)

Abstract

一种阀组件及一种压缩机，其阀组件（100、200、300）包括：阀片（110），阀挡（120、220、），阀挡（120、220）包括保持部（122、222）和构造成限制阀片（110）的位移范围的限位部（124、224）；以及安装件（130），安装件（130）构造成将阀片（110）和阀挡（120、220）安装至固定部件，安装件（130）包括延伸穿过第一安装孔（116）和第二安装孔（126）并且延伸至固定部件的连接部（132）以及抵靠阀挡（120、220）设置的紧固部（134），其中，从保持部（122、222）与限位部（124、224）的交界线到第二安装孔（126）的中心面的第一距离（A）大于从紧固部（134）的靠近限位部（124）的有效紧固端部到第二安装孔（126）的中心面的第二距离（B），第二安装孔（126）的中心面延伸穿过第二安装孔（126）的中心轴线且平行于交界线，有效紧固端部为紧固部（134）与阀挡（120、220）相接触的部分的距离中心面最远的端部。该阀组件能够减小或消除阀片的磨损以提高可靠性。

Description

阀组件及压缩机
本申请要求以下中国专利申请的优先权：于2020年4月30日提交中国专利局的申请号为202010365060.9、发明创造名称为“阀组件及压缩机”的中国专利申请；于2020年4月30日提交中国专利局的申请号为202020713317.0、发明创造名称为“阀组件及压缩机”的中国专利申请。这些专利申请的全部内容通过引用结合在本申请中。
技术领域
本公开涉及一种阀组件及一种包括该阀组件的压缩机。
背景技术
本部分的内容仅提供了与本公开相关的背景信息，其可能并不构成现有技术。
为了提高涡旋压缩机在欠压缩比工况下的压缩效率，通常在压缩机的涡旋组件的排气口处安装有单向阀以防止高温高压的制冷剂气体反灌至涡旋组件内部，进而导致制冷剂气体的重复压缩。单向阀通常包括阀挡以及布置在阀挡下方的阀片，其中，阀片能够在流体压力的作用下打开或者封闭流体通孔，阀挡能够用以限制阀片的位移范围。
然而，在压缩机的实际使用中，存在因单向阀失效而导致压缩机效率降低或甚至无法正常运行的情况，因此需要提供一种提高可靠性的阀组件。
发明内容
本公开的一个或多个实施方式的目的是提供一种减小或消除阀片磨损以具有高可靠性的阀组件。
根据本公开的一个方面，提供了一种阀组件，所述阀组件安装至设置有流体通孔的固定部件，并且所述阀组件包括：阀片，所述阀片构造成可位于打开所述流体通孔的打开位置与关闭所述流体通孔的关闭位置，并且所述阀片形成有第一安装孔；阀挡，所述阀挡包括保持部和构造成限制所述阀片的位移范围 的限位部，所述保持部具有抵靠所述阀片的平直表面，所述限位部具有从所述保持部远离所述阀片延伸的倾斜表面，并且所述阀挡形成有第二安装孔；以及安装件，所述安装件构造成将所述阀片和所述阀挡安装至所述固定部件，所述安装件包括延伸穿过所述第一安装孔和所述第二安装孔并且延伸至所述固定部件的连接部以及抵靠所述阀挡设置的紧固部，其特征在于，从所述保持部与所述限位部的交界线到所述第二安装孔的中心面的第一距离大于从所述紧固部的靠近所述限位部的有效紧固端部到所述第二安装孔的中心面的第二距离，所述第二安装孔的中心面延伸穿过所述第二安装孔的中心轴线且平行于所述交界线，所述有效紧固端部为所述紧固部与所述阀挡相接触的部分的距离所述中心面最远的端部。
根据本公开的一个方面，所述紧固部包括紧固头部和紧固垫片，其中，所述紧固头部向所述阀挡和所述阀片施加紧固力，所述紧固垫片夹持在所述紧固头部与所述阀挡之间。
根据本公开的一个方面，所述紧固垫片的与所述阀挡相接触的部分的距离所述中心面最远的端部充当所述有效紧固端部。
根据本公开的一个方面，所述阀片包括相邻布置的第一阀片和第二阀片，并且所述第一阀片设置在所述阀挡与所述第二阀片之间，所述第二阀片设置在所述第一阀片与所述固定部件之间。
根据本公开的一个方面，所述保持部设置有用于容纳所述紧固部的凹部。
根据本公开的一个方面，所述限位部沿第一方向从所述保持部延伸，所述保持部在垂直于所述第一方向的第二方向上关于所述第二安装孔对称地设置有两个销，所述销穿过形成在所述阀片上的销孔以防止所述阀片发生偏移。
根据本公开的一个方面，所述限位部的倾斜表面形成为弧形的倾斜表面。
根据本公开的一个方面，所述第一距离与所述第二距离的比值小于1.3。
根据本公开的另一方面，提供了一种包括上述阀组件的压缩机。
根据本公开的另一方面，所述压缩机为涡旋压缩机，所述涡旋压缩机包括适于压缩工作流体的压缩机构以及适于将所述涡旋压缩机的内部空间分隔未高压区域和低压区域的消音盖，以及所述固定部件安装在所述消音盖的通孔或者所述涡旋压缩机的排气口处，并且所述流体通孔与所述压缩机构的中央压缩腔流体连通。
附图说明
通过以下参照附图的描述，本公开的一个或几个实施方式的特征和优点将变得更加容易理解。这里所描述的附图仅是出于说明目的而非意图以任何方式限制本公开的范围，附图并非按比例绘制，并且一些特征可能被放大或缩小以显示特定部件的细节。在附图中：
图1为示意性地示出了应用有根据比较示例的阀组件的涡旋压缩机的剖视图；
图2和图3为示意性地示出了根据比较示例的阀组件的立体图；
图4为示意性地示出了根据本公开的第一实施方式的阀组件的剖视图；
图5a和图5b为示出了根据对比示例的阀组件及根据本公开的第一实施方式的阀组件的受磨损分析的示意图；
图6为示意性地示出了根据本公开的第一实施方式的阀组件的剖视图；以及
图7为示意性地示出了根据本公开的阀组件的安装件的替代性实施方式的剖视图。
具体实施方式
下面对本公开各实施方式的描述仅仅是示例性的，而绝不是对本公开及其应用或用法的限制。在各个附图中采用相同的附图标记来表示相同的部件，因此相同部件的构造将不再重复描述。
下面将参照图1来描述涡旋压缩机1的基本构造和原理。
如图1所示，压缩机1包括大致封闭的壳体20。壳体20可以由大致圆筒形的本体部22、设置在本体部22的一端的顶盖24、设置在本体部22的另一端的底盖26构成。在顶盖24和本体部22之间设置有隔板30以将壳体20的内部空间分隔成低压的流体吸入腔21和高压的流体排出腔23。隔板30和顶盖24之间的空间构成流体排出腔23，而隔板30、本体部22和底盖之间的空 间构成流体吸入腔21。在流体吸入腔21的一侧设置有用于吸入流体的进气接头，在流体排出腔23的一侧设置有用于排出压缩后的流体的排气接头。
在壳体20中设置有压缩机构和用于驱动压缩机构的驱动机构。压缩机构从壳体20的流体吸入腔21吸入流体并且将流体压缩后排出到壳体20的流体排出腔23中。更具体地，参见图1，压缩机构例如可以包括定涡旋40和动涡旋50。动涡旋50包括端板54和形成在端板一侧的螺旋状的涡卷56。定涡旋40包括端板44和形成在端板一侧的螺旋状的涡卷46，端板44包括形成在端板的大致中央位置处的排气口42。定涡旋40的涡卷46和动涡旋50的涡卷56相互啮合并且构成一系列体积从径向外侧向径向内侧逐渐减小的压缩腔以对流体进行压缩。通过位于径向最外侧的压缩腔吸入被压缩流体，并通过径向最内侧的压缩腔排出压缩后的流体。
如图1所示，经过定涡旋40和动涡旋50压缩后的工作流体通过排气口42以及隔板(消音盖)30的通孔朝向高压的流体排出腔23流动，为了防止高压侧的工作流体回流到压缩机构中，在例如消音盖30的通孔处或者在压缩机构的排气口相邻上方(参见图1，在定涡旋40的端板44的上侧的由定涡旋40的毂部限定的排气空间中)设置有阀组件100。阀组件100构造成允许压缩机构的压缩腔中的工作流体流动到高压侧，但是阻止高压侧的工作流体回流到压缩腔中。
如图2具体所示，根据对比示例的阀组件100可以包括阀片110、阀挡120以及安装件130。阀片110可以包括上下布置的第一阀片110a和第二阀片110b，其中,第一阀片110a可以设置在阀挡120与第二阀片110b之间并且第二阀片110b可以设置在第一阀片110a与阀组件固定座60之间。参照图3，每个阀片均形成有固定部112和可动部114，可动部114构造成能够相对于固定部112移动以选择性地打开或关闭设置在固定座60处的流体通孔，固定部112可以具有第一安装孔116。在阀片110上方设置有用以限制阀片110的位移范围的阀挡120。阀挡120包括保持部122和从保持部122沿纵向(也称第一方向)延伸的限位部124，其中，保持部122具有抵靠阀片的平直表面并且保持部122具有第二安装孔126，限位部124具有从保持部远离阀片110延伸的倾斜表面。安装件130用以将阀片110和阀挡120安装至固定座60，并且安装件130可以包括连接部132和紧固部134。连接部132可以延伸穿过第一安装孔116和第二安装孔126并且固定至固定座60。紧固部134包括向阀挡120和阀片110施加紧固力的紧固头部136以及夹持在紧固头部136与阀挡120之间的紧固垫 片138。在图3的示例中，安装件130示例性地示出为包括螺栓和紧固垫片138，其中螺栓包括连接部132和紧固头部136。保持部122可以设置有用于容纳紧固部134的凹部以节约阀组件的安装空间，并且保持部122在与纵向方向垂直的横向方向(也称第二方向)上关于第二安装孔126对称地设置有两个销，销穿过形成在阀片上的销孔以防止阀片发生横向偏移(例如因旋转而发生横向偏移)。
在压缩机1的操作期间，工作流体被吸入到压缩机构中并且随着从径向最外位置流动至径向最内位置而被压缩，压缩后的流体通过流体通孔排出。当处于中央压缩腔中的流体的压力大于排出腔23中的流体压力时，阀片110下侧的压力大于上侧压力，阀片110在压力差作用下朝向打开位置移动，从而允许流体通过流体通孔排出。当容纳在中央压缩腔中的流体的压力小于排出腔23中的流体压力时，阀片110在弹性回复力及压力差作用下返回至关闭位置。
本申请的发明人发现，根据对比示例的阀组件100在使用时，阀片110容易发生磨损，在磨损严重的情况下甚至会使得阀片110发生断裂，从而使与中央压缩腔流体连通的流体通孔始终与高压侧连通。在此情况下，压缩后的工作流体会从高压侧回流至压缩腔中，使得压缩机对工作流体进行反复压缩，这显然会对压缩效率造成不利影响。
为了解决上述问题，本公开构想出了一种改进的阀组件，该阀组件能够有效地解决阀片的磨损问题，从而避免因阀组件的磨损失效影响压缩机的性能。
下面就结合图4至图7对根据本公开的阀组件及应用有该阀组件的压缩机做进一步详细的说明。
图4示意性地示出了根据本公开的第一实施方式的阀组件的剖视图。
如图4所示，根据本公开的示例性实施方式的阀组件200可以安装至固定座60(对应于根据本公开的固定部件)并且可以包括阀片110、具有第二安装孔226的阀挡220以及安装件130。根据本公开的示例性实施方式的阀组件200的阀片和安装件与根据对比示例的阀组件100的相应部件的结构和功能相同，在此不再赘述。
根据本公开的示例性实施方式的阀组件200的阀挡220与根据对比示例的阀组件100的阀挡120类似地构造成限制阀片110的位移范围并且包括保持部222和限位部224，其不同之处在于，与阀挡120的保持部122相比，阀挡220的保持部222具有增大的长度。以下，将参照图5a和图5b对其进行详细描述。
本公开的发明人发现，当压缩机运行时，阀片110的上下两个阀片110a和110b在打开位置和关闭位置往复运动。然而，由于两个阀片110a和110b弯曲的曲率半径不同，并且加之工作流体的影响，使得两个阀片不能完全同步地打开和关闭，这将不可避免地在两个阀片的可动部之间产生微小的相对位移。如示出根据比较示例的阀组件的图5a所示，直线L延伸穿过限位部124与保持部122之间的交界线(图5a中示出为交点O)，并且直线L与第二安装孔的中心轴线C平行，在直线L与阀片110相交的交点F1处，存在两阀片110a和110b因运动不同步而产生的相对位移。同时，当紧固部134向阀挡120和阀片110施加紧固力时，紧固力在阀片110上的作用点与紧固部134靠近限位部124的端部(侧端)E的位置对准。在根据对比示例的阀组件100中，从端部E到第二安装孔的中心轴线C的距离B与从限位部124与保持部122之间的交点O到中心轴线C的距离A相等，此时，紧固力在阀片110上的作用点恰好位于直线L上并且与交点F1重合。也就是说，在交点F1处，一方面阀片110a和110b受到紧固部134施加的向下的正压力作用，另一方面阀片110a和110b还存在有相对位移，这将导致阀片发生微动磨损，微动磨损在阀片响应于压缩机的运行而反复打开和关闭时不断累积，从而损坏阀片甚至使得阀片完全断裂，导致阀组件失效。本文中限位部与保持部之间的交界线指的是阀挡的限位部与保持部的分界线，即限位部与保持部分别位于交界线O的两侧并且以此为界，该交界线在剖视图中示出为交点O。
为此，根据本公开的发明人巧妙地构思了具有加长的保持部222的阀组件200。如图5b所示，由于保持部222相对于保持部122具有增大的长度，因此从限位部224与保持部222之间的交点O到从中心轴线C的距离(第一距离)A大于从紧固部134的端部(有效紧固端部)E到中心轴线C的距离(第二距离)B。在此情况下，当紧固部134向阀挡220和阀片110施加紧固力时，紧固力在阀片110上的作用点与端部E的位置对准并且与直线L错开。由此，在直线L与阀片110相交的交点F1处，仅存在两阀片110a和110b因运动不同步而产生的相对位移，而不存在由紧固部134施加的紧固力。以此方式，可以避免使阀片110发生微动磨损，从而提高阀组件的可靠性并且确保压缩机的工作效率。优选地，距离A可以处于距离B的1到1.3倍的范围内(不包括端值)。根据试验，发明人发现，距离A与距离B的这个比值可以有效地减小和避免微动磨损而且有利于最小化阀组件的改动从而易于制造并节约成本。另外，通过试验，申请人进一步发现，当距离A处于距离B的1.05到1.1倍的 这个范围内时，则各方面的效果更加突出。这里，需要说明的是，在本文中，端部E也称为紧固部的有效紧固端部。亦即，有效紧固端部指的是紧固部的靠近限位部的侧端，并且，在紧固部不规则设置的情况下(例如紧固部形成为具有多个端部的多角形结构)，则紧固端部指的是到多个端部中到穿过中心轴线C且平行于交界线O的中心面距离最远的端部，特别地，当紧固部沿竖向方向也呈不规则布置的情况下(例如紧固部形成为上宽下窄的结构时)，则有效紧固端部指的是紧固部与阀挡相接触的部分(即下侧较窄的部分)的距离中心面最远的端部。可以理解，紧固部与阀挡相接触的部分的上述端部有效地起到向阀挡的保持部和阀片施加紧固力的作用。当紧固部如图4所示包括紧固头部和紧固垫片两者时，紧固垫片与阀挡相接触的部分的距离中心面最远的端部充当有效紧固端部。
图6示出了根据本公开的第二实施方式的阀组件300的剖视图。阀组件300可以包括阀片110、阀挡120以及安装件330。根据本公开的第二实施方式的阀组件300的阀片和阀挡与根据对比示例的阀组件100的相应部件的结构和功能相同，在此不再赘述。并且，根据本公开的第二实施方式的阀组件300的安装件330与根据对比示例的阀组件100的安装件130类似地包括连接部332和紧固部334，其中，连接部332可以延伸穿过第一安装孔和第二安装孔并且固定至固定座60，并且紧固部334包括向阀挡120和阀片110施加紧固力的紧固头部336以及夹持在紧固头部336与阀挡120之间的紧固垫片338，安装件330与安装件130的不同之处在于，紧固垫片338具有与紧固垫片138相比减小的半径。
在根据本公开的第二实施方式的阀组件300中，由于紧固垫片338的半径减小，因此从交点O到中心轴线C的距离A大于从紧固垫片338的端部E到中心轴线C的距离B(在本实施方式中，紧固垫片338的端部E充当根据本公开的有效紧固端部)。此时，当紧固部334向阀挡120和阀片110施加紧固力时，紧固力在阀片110上的作用点与紧固垫片338的端部E的位置对准并且与直线L错开。由此，在直线L与阀片110相交的交点F1处，仅存在两阀片110a和110b因运动不同步而产生的相对位移，而不存在由紧固部334施加的紧固力。以此方式，可以避免使阀片110发生微动磨损，从而提高阀组件的可靠性并且确保压缩机的工作效率。在此需要说明的是，尽管在根据本公开的第一和第二实施方式中，安装件示例性地示出为包括螺栓和紧固垫片，其中螺栓包括连接部和紧固头部，但是本公开不限于此，安装件130’也可以包括铆钉和 紧固垫片(如图7所示)。
在根据本公开的第二实施方式的阀组件300中，可以直接地利用阀挡标准件及安装件标准件而无需对其进行改型，例如可以利用螺栓标准件和与较小尺寸的螺栓标准件配套的较小的垫片标准件。以此方式，可以以方便且节约成本的方式提供一种具有高的可靠性的阀组件。
尽管根据本公开的第二实施方式示例性地描述了阀组件300具有减小半径的紧固垫片338，但是本领域技术人员应当理解的是，阀组件也可以具有减小半径的紧固头部336，由于紧固头部336的半径减小，因此从交点O到中心轴线C的距离A大于从紧固头部336的端部到中心轴线C的距离B(在本变型中，紧固头部的端部充当根据本公开的有效紧固端部)。在此情况下，当紧固部334向阀挡120和阀片110施加紧固力时，紧固力在阀片110上的作用点与紧固头部336的端部的位置对准并且与直线L错开。由此，在交点F1处，仅存在两阀片110a和110b因运动不同步而产生的相对位移，而不存在由紧固部134施加的紧固力。当然，也可以使紧固垫片和紧固头部两者均具有减小的半径，或者甚至使紧固垫片的靠近阀挡的一部分具有减小的半径。此外，尽管在根据本公开的示例性实施方式中，安装件示出为包括紧固垫片，但是本公开不限于此，也可以省略紧固垫片而仅使用包含紧固头部和连接部的安装件。
在此，还应当指出的是，在本公开的示例性实施方式中描述了阀片110包括两个阀片110a和110b，但是本公开不限于此，阀片110也可以形成为单个阀片。在阀片110为单个阀片的情况下，由于阀片110在打开和关闭的过程中存在阀片110与上方的阀档之间的相对位移，因此也可能使得阀片110发生微动磨损，采用根据本公开的示例性实施方式的阀组件同样也可以解决这种单个阀片的磨损问题。当然，阀组件200优选地可以包括两个阀片110a和110b，在此情况下，即使一个阀片发生损坏或断裂，仍能使用另一个阀片进行选择性地打开或关闭流体通孔。由此，可以进一步减低阀组件失效的风险，防止工作流体返回至压缩腔，从而确保压缩机的工作效率。
尽管在此详细描述了本公开的各种实施方式，但是应该理解，本公开并不局限于这里详细描述和示出的具体实施方式，在不偏离本公开的实质和范围的情况下可由本领域的技术人员实现其它的变型和变体，例如，阀组件也可以应用于除了涡旋压缩机之外的其他压缩机并且也可以应用于压缩机之外的任何其他需要单向阀的机械。所有这些变型和变体都落入本公开的范围内。而且， 所有在此描述的构件都可以由其他技术性上等同的构件来代替。

Claims (10)

  1. 一种阀组件(200，300)，所述阀组件安装至设置有流体通孔的固定部件(60)，并且所述阀组件包括：
    阀片(110a,110b)，所述阀片构造成可位于打开所述流体通孔的打开位置与关闭所述流体通孔的关闭位置，并且所述阀片形成有第一安装孔(116)；
    阀挡(120，220)，所述阀挡包括保持部(122,222)和构造成限制所述阀片(110a,110b)的位移范围的限位部(124,224)，所述保持部具有抵靠所述阀片的平直表面，所述限位部具有从所述保持部远离所述阀片延伸的倾斜表面，并且所述阀挡形成有第二安装孔(126，226)；以及
    安装件(130，330)，所述安装件构造成将所述阀片和所述阀挡安装至所述固定部件(60)，所述安装件包括延伸穿过所述第一安装孔(116)和所述第二安装孔(126，226)并且延伸至所述固定部件的连接部(132，332)以及抵靠所述阀挡设置的紧固部(134，334)，
    其特征在于，从所述保持部(122,222)与所述限位部(124,224)的交界线(O)到所述第二安装孔的中心面的第一距离(A)大于从所述紧固部(134，334)的靠近所述限位部(124,224)的有效紧固端部(E)到所述第二安装孔的中心面的第二距离(B)，所述第二安装孔的中心面延伸穿过所述第二安装孔的中心轴线(C)且平行于所述交界线(O)，所述有效紧固端部为所述紧固部与所述阀挡相接触的部分的距离所述中心面最远的端部。
  2. 根据权利要求1所述的阀组件，其中，
    所述紧固部(134，334)包括紧固头部(136，336)和紧固垫片(138，338)，其中，所述紧固头部(134，334)向所述阀挡和所述阀片施加紧固力，所述紧固垫片(138，338)夹持在所述紧固头部(136，336)与所述阀挡(120，220)之间。
  3. 根据权利要求2所述的阀组件，其中，
    所述紧固垫片的与所述阀挡相接触的部分的距离所述中心面最远的端部充当所述有效紧固端部(E)。
  4. 根据权利要求1所述的阀组件，其中，
    所述阀片(110a,110b)包括相邻布置的第一阀片(110a)和第二阀片(110b)，并且所述第一阀片(110a)设置在所述阀挡(120,220)与所述第二阀片之间，所述第二阀片(110b)设置在所述第一阀片与所述固定部件(60)之间。
  5. 根据权利要求1所述的阀组件，其中，
    所述保持部(122,222)设置有用于容纳所述紧固部的凹部。
  6. 根据权利要求1所述的阀组件，其中，
    所述限位部沿第一方向从所述保持部延伸，所述保持部(122,222)在垂直于所述第一方向的第二方向上关于所述第二安装孔对称地设置有两个销，所述销穿过形成在所述阀片上的销孔以防止所述阀片发生偏移。
  7. 根据权利要求1所述的阀组件，其中，
    所述限位部(124,224)的倾斜表面形成为弧形的倾斜表面。
  8. 根据权利要求1-7中的任一项所述的阀组件，其中，
    所述第一距离(A)与所述第二距离(B)的比值小于1.3。
  9. 一种压缩机，其特征在于，所述压缩机包括根据权利要求1-8中的任一项所述的阀组件。
  10. 根据权利要求9所述的压缩机，其中，
    所述压缩机为涡旋压缩机，所述涡旋压缩机包括适于压缩工作流体的压缩机构以及适于将所述涡旋压缩机的内部空间分隔未高压区域和低压区域的消音盖，以及
    所述固定部件安装在所述消音盖的通孔或者所述涡旋压缩机的排气口处，并且所述流体通孔与所述压缩机构的中央压缩腔流体连通。
PCT/CN2020/121412 2020-04-30 2020-10-16 阀组件及压缩机 WO2021218050A1 (zh)

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CN85201501U (zh) * 1985-05-18 1986-01-22 西安交通大学 用于2fl5ba型压缩机的排气舌簧阀
JPH08326939A (ja) * 1995-06-03 1996-12-10 Samsung Electronics Co Ltd 圧縮機の吐出弁装置
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US11754192B2 (en) * 2021-05-12 2023-09-12 Buerkert Werke Gmbh & Co. Kg Diaphragm valve and method of manufacturing the same

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