WO2015027824A1 - 调节器结构及离心式压缩机 - Google Patents

调节器结构及离心式压缩机 Download PDF

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Publication number
WO2015027824A1
WO2015027824A1 PCT/CN2014/084409 CN2014084409W WO2015027824A1 WO 2015027824 A1 WO2015027824 A1 WO 2015027824A1 CN 2014084409 W CN2014084409 W CN 2014084409W WO 2015027824 A1 WO2015027824 A1 WO 2015027824A1
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WO
WIPO (PCT)
Prior art keywords
regulator
driven gear
adjuster
elongated
gear
Prior art date
Application number
PCT/CN2014/084409
Other languages
English (en)
French (fr)
Inventor
蒋彩云
张治平
钟瑞兴
蒋楠
谢蓉
闫秀兵
王宏兴
Original Assignee
珠海格力电器股份有限公司
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
Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Priority to JP2016537108A priority Critical patent/JP6343346B2/ja
Priority to EP14840668.9A priority patent/EP3040562B1/en
Priority to US14/914,937 priority patent/US10082147B2/en
Priority to ES14840668.9T priority patent/ES2663502T3/es
Publication of WO2015027824A1 publication Critical patent/WO2015027824A1/zh
Priority to PH12016500365A priority patent/PH12016500365B1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/002—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying geometry within the pumps, e.g. by adjusting vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0253—Surge control by throttling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type

Definitions

  • the present invention relates to a regulator structure, and more particularly to a structure for adjusting the width of an outlet of a centrifugal compressor impeller and a centrifugal compressor. Background technique
  • the regulator is installed at the outlet of the impeller to form an adjustable section of the width, and the width of the impeller outlet is adjusted according to the operation of the unit, so that the unit can maintain the highest efficiency in a wide range.
  • the conventional centrifugal compressor regulator is generally interlocked with the impeller adjustment mechanism, and the structure is not independent, so the control is not accurate enough; and the adjustable range of the impeller is small, and cannot be widely applied to various working conditions of the compressor.
  • the invention provides a regulator structure, comprising a vane diffuser, a motor, a driving gear, a driven gear and an adjusting mechanism; the motor can rotate forward and backward; the driving gear meshes with the driven gear;
  • the adjustment mechanism includes a regulator, a support member and a regulator slide member
  • the driven gear is set on the adjuster, and the adjuster is sleeved on the support member;
  • An elongated through hole is disposed on the driven gear, and the elongated through hole extends along an axis of the driven gear; the adjuster sliding member is fixed to the adjuster through the elongated through hole;
  • the vane diffuser is fixed on the support body and has an internal thread
  • the adjuster is provided with an external thread to engage with the internal thread of the vane diffuser
  • the motor drives the driving gear to rotate, the driving gear drives the driven gear to rotate; the driven gear rotates to push the regulator sliding member to move, and the regulator sliding member drives the adjusting device to rotate
  • the vane diffuser is rotated such that the adjuster moves in the axial direction of the adjuster.
  • the regulator structure further includes a driven gear limiter;
  • the driven gear limiter is disposed on the adjuster and disposed between the driven gear and the vane diffuser.
  • a bearing is disposed between the driven gear and the driven gear limiter.
  • the outer circumference of one end of the adjuster is provided with a groove matching the elongated through hole, the axis of the groove being perpendicular to the axis of the adjuster;
  • the adjuster slider is fixed in the recess of the adjuster through the elongated through hole.
  • the elongated through holes are at least two, and at least two of the elongated through holes are evenly arranged along a circumference of the driven gear;
  • the groove matches the number of the elongated through holes.
  • the groove has an internal thread
  • the adjuster slider is a screw
  • the inner thread of the groove is engaged with the external thread of the adjuster slider.
  • the outer circumference of the support member is provided with a sealing groove; and a sealing groove is disposed in the sealing groove.
  • the length of the adjuster is greater than the length of the support.
  • a centrifugal compressor of the present invention includes an impeller and the regulator structure.
  • the externally threaded end of the regulator of the regulator structure is placed at the outlet of the impeller; when the motor drives the driving gear to rotate in the forward direction, the driven gear is rotated in the forward direction.
  • the externally threaded end of the regulator continues to retract until the impeller outlet is fully opened; when the motor drives the driving gear to rotate in the reverse direction, the driven gear is reversely rotated, and the regulator is moved to the The externally threaded end continues to extend until the impeller outlet is completely closed.
  • the utility model has the advantages that: the regulator structure and the centrifugal compressor can obtain a large adjustment range, and the application range is wide; the outlet can be completely closed to prevent the reverse flow of the refrigerant gas, and the impeller is reversed. Turning, and impairing the impeller; independent control, less transmission links, higher transmission efficiency and reliability; can maintain the direction and speed of the airflow at the inlet of the diffuser of the vane without changing, effectively reducing the impact loss, and effectively preventing surge Occurs; The overall structure of the regulator structure is compact, easy to manufacture and easy to modify.
  • Figure 1 is a schematic view showing the structure of the regulator of the first embodiment of the present invention fully opened;
  • FIG. 2 is a partial schematic view showing the structure of the regulator of the first embodiment of the present invention not fully opened;
  • Figure 3 is a partial schematic view showing the structure of the regulator of the first embodiment of the present invention completely closed;
  • Figure 4 is a schematic view showing the structure of the regulator of the second embodiment of the present invention fully opened.
  • FIG. 1 is a schematic diagram of the regulator structure of the first embodiment of the present invention fully opened.
  • the regulator structure includes a motor 20 , a driving gear 31 , a driven gear 32 , a vane diffuser 42 and an adjustment thereof . mechanism.
  • the motor 20 can achieve forward and reverse rotation.
  • the drive gear 31 and the driven gear 32 are preferably bevel gears.
  • the driving gear 31 is connected to the motor 20, and the motor 20 drives the driving gear 31 to rotate. Due to the meshing relationship between the driving gear 31 and the driven gear 32, the driven gear 32 is also synchronized. Turn.
  • the adjustment mechanism includes a regulator 41, a support member 43 and a regulator slider 47.
  • the outer shape of the support member 43 is cylindrical.
  • the adjuster 41 is formed by rotation, has a through hole at a center thereof, and the adjuster 41 is fitted on the outer profile of the support member 43.
  • the length of the adjuster 41 is greater than the length of the support member 43.
  • a support member 43 is placed in the middle of the adjuster 41, and being placed in the middle enables the adjuster 41 to receive a relatively balanced support.
  • the motor 20 drives the driving gear 31 to rotate, the driving gear 31 drives the driven gear 32 to rotate; the driven gear 32 pushes the regulator sliding member 47 to move, and the regulator sliding member 47 drives
  • the adjuster 41 is rotated relative to the vane diffuser 42 such that the adjuster 41 moves in the axial direction of the adjuster 41.
  • the driven gear 32 is sleeved on the adjuster 41, and the axes of the two are coincident; the driven gear 32 has an elongated through hole, and the axis of the elongated through hole and the driven gear 32 The axis is perpendicular, and the elongated through hole extends along an axis of the driven gear 32.
  • the elongated through holes are arranged at least two on the driven gear 32. Considering the difficulty of the machining process and the balance of forces, it is preferred to use two of the elongated through holes.
  • the adjuster slider 47 is fixedly coupled to the adjuster 41 through an elongated through hole of the driven gear 32, and may be fixed by welding or integrally formed with the adjuster 41.
  • a groove is provided on the adjuster 41 near one end of the driven gear 32, the groove being the same as the number of the elongated through holes, and the positions arranged on the circumference are matched.
  • the adjuster slider 47 is coupled to the recess through the elongated through hole of the driven gear 32; this is easier to machine and the mounting is stable.
  • the groove may have a thread
  • the adjuster slider 47 may also be provided with a thread
  • the adjuster slider 47 and the groove are reliably connected by a thread
  • the adjuster slider 47 is a screw or a screw
  • the adjuster 41 and the adjuster slider 47 as a whole slide along the axial direction of the adjuster 41 in the elongated through hole, and the length of the elongated through hole determines the axial slip the distance.
  • An end of the adjuster 41 remote from the driven gear 32 has an external thread
  • the vane diffuser 42 has an internal thread
  • the vane diffuser 42 is fitted on the external thread of the adjuster 41, and The adjuster 41 is screwed; at the same time, the vane diffuser 42 is fixed to the support member 43.
  • the external thread on the adjuster 41 can be designed according to actual needs, and the length of the elongated through hole on the driven gear 32 corresponding thereto can be adjusted, so that a longer range of adjustment can be realized. Different needs in the actual situation.
  • the engagement with the driving gear 31 is ensured, and the driven gear limiting member 44 is disposed on the adjuster 41, and the driven gear is limited.
  • the center of the member 44 has a through hole that fits over the adjuster 41.
  • the adjuster structure further includes a limit fastener 46 that secures the driven gear limit member 44 to the housing 10.
  • the limit fastener 46 may be a screw, a locating pin or a key. A plurality of the limit fasteners 46 may be disposed along the outer circumference of the driven gear limiter 44.
  • a sealing groove is provided on the outer periphery of the support member 43 for placing a sealing jaw 48 for ensuring a good seal of the adjuster 41 and the support member 43.
  • the regulator structure is mounted to a centrifugal compressor having a housing 10 to which the support member 43 is fixed, the externally threaded end of the adjuster 41 being mounted Near the exit of the impeller 50.
  • the axial movement of the adjuster 41 causes expansion and contraction of the adjuster 41, which in turn changes the outlet width of the impeller 50.
  • FIG. 2 it is a partial schematic view of the regulator structure of the first embodiment of the present invention which is not fully opened.
  • the regulator 41 of the regulator structure is in an incompletely opened state, and the double-headed arrow indicates In the direction in which the regulator 41 moves along its axis, a one-way arrow indicates the flow direction of the refrigerant in the centrifugal compressor.
  • FIG. 3 it is a partial schematic view showing the structure of the regulator of the first embodiment of the present invention being completely closed.
  • the outlet of the impeller 50 is completely closed to prevent the refrigerant gas from flowing backward, causing the impeller 50 to reverse.
  • the regulator structure avoids the use of a check valve to prevent the impeller 50 from reversing resulting in damage.
  • FIG. 4 is a schematic diagram of the regulator structure of the second embodiment of the present invention being completely opened, the difference between this embodiment and the first embodiment shown in FIG. 1 is that the regulator structure is in the Driven gear 32 and the vane diffuser A bearing 49 is provided between 42.
  • the bearing 49 is preferably a thrust bearing, and the frictional resistance using the thrust bearing is small and the working state is better.
  • the outlet width of the impeller 50 is precisely adjusted to form a continuous adjustable width that allows the centrifugal compressor to operate at maximum efficiency.
  • the regulator structure is independently controlled, the transmission link is small, and the transmission efficiency and reliability are high.
  • the adjustment of the regulator structure can maintain the direction and speed of the airflow at the inlet of the vane diffuser 42 without changing, effectively reduce the impact loss, and effectively prevent the occurrence of surge, and has high reliability, so that the centrifugal compressor The scope of work has increased.
  • the overall structure of the regulator structure is compact and easy to manufacture and manufacture.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种调节器结构，该调节器结构包括叶片扩压器（42）、电机（20）、主动齿轮（31）、从动齿轮（32）与调节机构；电机（20）可正反转动；调节机构包括调节器（41）、支撑件（43）与调节器滑动件（47）；从动齿轮（32）套装在调节器（41）上，调节器（41）套装在支撑件（43）上；从动齿轮（32）上设置长形通孔，长形通孔沿从动齿轮（31）的轴线延伸设置；调节器滑动件（47）通过长形通孔与调节器（41）固定；叶片扩压器（42）固定在支撑体上；电机（20）驱动主动齿轮（31）旋转，主动齿轮（31）带动从动齿轮（32）旋转；从动齿轮（32）旋转，推动调节器滑动件（47）运动，调节器滑动件（47）带动调节器（41）相对于叶片扩压器（42）旋转，使得调节器（41）沿调节器的轴线方向移动，获得较大调节范围。以及一种带有该调节器的离心式压缩机。

Description

调节器结构及离心式压缩机
相关申请
本专利申请要求 2013年 8月 26 日申请的， 申请号为 201310377440. 4 , 名称为 "调节器 结构及离心式压塑机" 的中国专利申请的优先权， 在此将其全文引入作为参考。
技术领域
本发明涉及一种调节器结构， 特别是涉及一种用于调节离心式压缩机叶轮出口宽度的结 构及离心式压缩机。 背景技术
现有技术中， 对于离心式压缩机， 将调节器安装在叶轮出口处， 形成一个宽度可调节段， 并按照机组运行情况，调节叶轮出口宽度， 达到使机组在较宽范围保持最高效率运行的目的。 现有离心式压缩机用调节器一般与叶轮调节机构联动， 结构不独立， 所以控制不够精确； 而 且叶轮可调节的宽度范围较小， 不能广泛适用于压缩机的各种工况。
鉴于上述缺陷， 本发明人经过长时间的研究和实践终于获得了本发明创造。 发明内容
基于此， 有必要提供一种能实现较大调节范围的调节器结构及离心式压缩机。
本发明提供一种调节器结构， 包括叶片扩压器、 电机、 主动齿轮、 从动齿轮与调节机构； 所述电机可正反转动； 所述主动齿轮与所述从动齿轮啮合；
所述调节机构包括调节器、 支撑件与调节器滑动件；
所述从动齿轮套装在所述调节器上， 所述调节器套装在所述支撑件上；
所述从动齿轮上设置长形通孔， 所述长形通孔沿所述从动齿轮的轴线延伸设置； 所述调节器滑动件通过所述长形通孔与所述调节器固定；
所述叶片扩压器固定在支撑体上， 并具有内螺紋；
所述调节器上设置有外螺紋， 与叶片扩压器的内螺紋啮合；
所述电机驱动所述主动齿轮旋转， 所述主动齿轮带动所述从动齿轮旋转； 所述从动齿轮 旋转， 推动所述调节器滑动件运动， 所述调节器滑动件带动所述调节器相对于所述叶片扩压 器旋转， 使得所述调节器沿所述调节器的轴线方向移动。
在其中一些实施例中， 所述的调节器结构还包括从动齿轮限位件； 所述从动齿轮限位件套装在所述调节器上， 置于所述从动齿轮与所述叶片扩压器之间。 在其中一些实施例中， 在所述从动齿轮与所述从动齿轮限位件之间设置轴承。
在其中一些实施例中， 所述调节器一端的外周上设置有与所述长形通孔相匹配的凹槽， 所述凹槽的轴线与所述调节器的轴线垂直；
所述调节器滑动件通过所述长形通孔固定在所述调节器的凹槽内。
在其中一些实施例中， 所述长形通孔至少为两个， 至少为两个的所述长形通孔沿所述从 动齿轮的圆周均匀布置；
所述凹槽与所述长形通孔的数量相匹配。
在其中一些实施例中， 所述凹槽有内螺紋， 所述调节器滑动件为螺杆， 所述凹槽的内螺 紋与所述调节器滑动件的外螺紋啮合固定。
在其中一些实施例中， 所述支撑件的外周设置密封槽； 在所述密封槽内设置密封圏。 在其中一些实施例中， 所述调节器的长度大于所述支撑件的长度。
本发明的一种离心式压缩机， 包括叶轮与所述的调节器结构。
在其中一些实施例中， 所述调节器结构的调节器的外螺紋端置于所述叶轮的出口处； 所述电机驱动所述主动齿轮正向旋转时， 带动所述从动齿轮正向旋转， 所述调节器的外 螺紋端持续回缩， 直至所述叶轮出口完全打开； 所述电机驱动所述主动齿轮反向旋转时， 带 动所述从动齿轮反向旋转， 所述调节器向所述外螺紋端持续伸出， 直至所述叶轮出口完全封 闭。
与现有技术比较本发明的有益效果在于： 该调节器结构以及该离心式压缩机， 能得到较 大的调节范围， 适用范围很广； 出口可以完全封闭， 防止冷媒气体倒流， 致叶轮出现反转， 而损害叶轮； 独立控制， 传动环节少， 传动效率和可靠性较高； 能保持叶片扩压器入口处的 气流的方向、 速度不发生变化， 有效降低冲击损失， 并有效防止喘振的发生； 调节器结构的 整体结构紧凑， 加工制造且改装方便。
附图说明
图 1为本发明的第一实施例的调节器结构完全打开的示意图；
图 2为本发明的第一实施例的调节器结构未完全打开的局部示意图；
图 3为本发明的第一实施例的调节器结构完全关闭的局部示意图；
图 4为本发明的第二实施例的调节器结构完全打开的示意图。
具体实施方式
为了解决调节范围较小的问题， 提出了一种调节器结构。 以下结合附图， 对本发明上述的和另外的技术特征和优点作更详细的说明。 请参阅图 1所示， 其为本发明的第一实施例的调节器结构完全打开的示意图， 所述调节 器结构包括电机 20、 主动齿轮 31、 从动齿轮 32、 叶片扩压器 42及调节机构。
所述电机 20可以实现正反转。
所述主动齿轮 31和所述从动齿轮 32优选为锥齿轮。
所述主动齿轮 31与所述电机 20相连接， 所述电机 20驱动所述主动齿轮 31转动， 由于 所述主动齿轮 31和所述从动齿轮 32的啮合关系， 所述从动齿轮 32也同步转动。
所述调节机构包括调节器 41、 支撑件 43与调节器滑动件 47。
所述支撑件 43的外廓为圆柱形。
所述调节器 41经旋转形成， 其中心具有通孔， 所述调节器 41套装在所述支撑件 43的外 廓上， 所述调节器 41的长度大于所述支撑件 43的长度， 所述支撑件 43置于所述调节器 41 的中部， 置于中部能够使所述调节器 41得到比较平衡的支撑。
所述电机 20驱动所述主动齿轮 31旋转， 所述主动齿轮 31带动所述从动齿轮 32旋转； 所述从动齿轮 32推动所述调节器滑动件 47运动， 所述调节器滑动件 47带动所述调节器 41 相对于所述叶片扩压器 42旋转， 使得所述调节器 41沿所述调节器 41的轴线方向移动。
所述从动齿轮 32套装在所述调节器 41上， 两者的轴线重合； 所述从动齿轮 32上具有长 形通孔， 所述长形通孔的轴线与所述从动齿轮 32的轴线垂直， 所述长形通孔沿所述从动齿轮 32 的轴线延伸布置。 所述长形通孔在所述从动齿轮 32上至少布置两个。 考虑加工工艺难度 及受力平衡， 优先使用两个所述长形通孔。
所述调节器滑动件 47通过所述从动齿轮 32的长形通孔固定连接到所述调节器 41 , 可以 通过焊接方式固定或与所述调节器 41一体成型。
较优地， 在所述调节器 41上靠近所述从动齿轮 32的一端设置凹槽， 所述凹槽与所述长 形通孔的数量相同， 在圆周上布置的位置相匹配。 所述调节器滑动件 47 通过所述从动齿轮 32的所述长形通孔连接到所述凹槽； 这种方式较容易加工， 且安装固定稳定。
所述凹槽可以具有螺紋， 所述调节器滑动件 47 上也可以设置螺紋， 所述调节器滑动件 47与所述凹槽通过螺紋可靠连接； 所述调节器滑动件 47为螺杆或者螺钉； 所述调节器 41与 所述调节器滑动件 47作为一个整体在所述长形通孔内沿所述调节器 41的轴向滑移， 所述长 形通孔的长度决定了轴向滑移的距离。
所述调节器 41上远离所述从动齿轮 32的一端具有外螺紋，所述叶片扩压器 42具有内螺 紋，所述叶片扩压器 42套装在所述调节器 41的外螺紋上，与所述调节器 41螺紋连接； 同时， 所述叶片扩压器 42固定在所述支撑件 43上。
根据以上的描述， 当所述从动齿轮 32的旋转带动所述调节器 41旋转时， 由于所述调节 器 41与所述叶片扩压器 42的螺紋配合， 而所述叶片扩压器 42位置固定， 所述调节器 41的 旋转导致其沿轴向移动， 在所述叶片扩压器 42的内螺紋内沿轴向推进。 当所述电机 20反向 旋转时， 带动所述主动齿轮 31、 所述从动齿轮 32、 所述调节器 41反向旋转， 所述调节器 41 在所述叶片扩压器 42的内螺紋内沿轴向退回。
所述调节器 41上外螺紋可以根据实际需要设计长度，并调整与之相对应的所述从动齿轮 32上的所述长形通孔的长度，这样就可以实现较长范围的调节，适应实际情况中的不同需求。
较优地， 为防止所述从动齿轮 32沿轴向移动， 保证与所述主动齿轮 31的啮合， 在所述 调节器 41上设置从动齿轮限位件 44 , 所述从动齿轮限位件 44的中心具有通孔， 套装在所述 调节器 41上。
较优地， 所述调节器结构还包括限位紧固件 46 , 所述限位紧固件 46将所述从动齿轮限 位件 44固定在所述壳体 10上。
所述限位紧固件 46可以为螺钉、 定位销或键的结构， 可以沿所述从动齿轮限位件 44的 外周设置多处所述限位紧固件 46。
较优地， 在所述支撑件 43外廓上具有密封槽， 用于放置密封圏 48 , 用于保证所述调节 器 41与所述支撑件 43的良好密封。
将所述调节器结构安装到离心式压缩机上， 所述离心式压缩机具有壳体 10, 将所述支撑 件 43固定在所述壳体 10上， 所述调节器 41的外螺紋端安装在叶轮 50的出口附近。 所述调 节器 41的轴向移动导致所述调节器 41的伸缩， 进而改变所述叶轮 50的出口宽度。
所述电机 20驱动所述主动齿轮 31正向旋转时， 带动所述从动齿轮 32正向旋转， 所述调 节器 41的外螺紋端持续回缩， 直至所述叶轮 50的出口完全打开。 图 1中为所述叶轮 50的出 口宽度最大的状态。
请参阅图 2所示， 其为本发明的第一实施例的调节器结构未完全打开的局部示意图， 所 述调节器结构的所述调节器 41处于未完全打开的状态， 图中双向箭头表示所述调节器 41的 沿其轴线移动的方向， 单向箭头表示离心式压缩机中冷媒的流动方向。
请参阅图 3所示， 其为本发明的第一实施例的调节器结构完全关闭的局部示意图， 所述 电机 20驱动所述主动齿轮 31反向旋转时， 带动所述从动齿轮 32反向旋转， 所述调节器 41 向所述外螺紋端持续伸出， 直至所述叶轮 50的出口完全封闭。
当所述调节器 41伸缩到最大位置时， 所述叶轮 50的出口完全被封闭， 防止冷媒气体倒 流， 使所述叶轮 50 出现反转的问题。 所述调节器结构避免了止回阀的使用， 防止所述叶轮 50反转导致损害。
请参阅图 4所示， 其为本发明的第二实施例的调节器结构完全打开的示意图， 本实施例 与图 1所示的第一实施例的区别在于：所述调节器结构在所述从动齿轮 32与所述叶片扩压器 42之间设置轴承 49。
所述轴承 49优选为推力轴承， 使用推力轴承的摩擦阻力较小， 工作状态更好。
常规离心机已经形成系列化批量生产的成熟产品， 对常规离心式压缩机现有的叶片扩压 器和壳体稍加改装， 利用现有空间即可安装所述调节器结构。将所述调节器 41的尺寸稍加改 变即可适应不同直径所述叶轮 50, 可以适用于不同功率的离心式压缩机， 适用范围很广。
根据使用工况， 精确调节所述叶轮 50的出口宽度， 形成连续的可调节宽度， 使所述离心 式压缩机保持在最高效率下运行。
所述调节器结构为独立控制， 传动环节少， 传动效率和可靠性较高。 所述调节器结构的 调节能保持所述叶片扩压器 42入口处的气流的方向、 速度不发生变化， 有效降低冲击损失， 并有效防止喘振的发生， 可靠性高， 使离心式压缩机工作范围加大。 所述调节器结构的整体 结构紧凑， 加工制造方便。
以上所述实施例仅表达了本发明的几种实施方式， 其描述较为具体和详细， 但并不能因 此而理解为对本发明专利范围的限制。 应当指出的是， 对于本领域的普通技术人员来说， 在 不脱离本发明构思的前提下， 还可以做出若千变形和改进， 这些都属于本发明的保护范围。

Claims

权利要求
1、 一种调节器结构， 包括叶片扩压器， 其特征在于， 还包括电机、 主动齿轮、 从动齿轮 与调节机构；
所述电机可正反转动； 所述主动齿轮与所述从动齿轮啮合；
所述调节机构包括调节器、 支撑件与调节器滑动件；
所述从动齿轮套装在所述调节器上， 所述调节器套装在所述支撑件上；
所述从动齿轮上设置长形通孔， 所述长形通孔沿所述从动齿轮的轴线延伸设置； 所述调节器滑动件通过所述长形通孔与所述调节器固定；
所述叶片扩压器固定在支撑体上， 并具有内螺紋；
所述调节器上设置有外螺紋， 与叶片扩压器的内螺紋啮合；
所述电机驱动所述主动齿轮旋转， 所述主动齿轮带动所述从动齿轮旋转； 所述从动齿轮 旋转， 推动所述调节器滑动件运动， 所述调节器滑动件带动所述调节器相对于所述叶片扩压 器旋转， 使得所述调节器沿所述调节器的轴线方向移动。
2、 根据权利要求 1所述的调节器结构， 其特征在于， 还包括从动齿轮限位件； 所述从动齿轮限位件套装在所述调节器上， 置于所述从动齿轮与所述叶片扩压器之间。
3、 根据权利要求 2所述的调节器结构， 其特征在于， 在所述从动齿轮与所述从动齿轮限 位件之间设置轴承。
4、 根据权利要求 1至 3任一项所述的调节器结构， 其特征在于， 所述调节器一端的外周 上设置有与所述长形通孔相匹配的凹槽， 所述凹槽的轴线与所述调节器的轴线垂直；
所述调节器滑动件通过所述长形通孔固定在所述调节器的凹槽内。
5、 根据权利要求 4所述的调节器结构， 其特征在于， 所述长形通孔至少为两个， 至少为 两个的所述长形通孔沿所述从动齿轮的圆周均匀布置；
所述凹槽与所述长形通孔的数量相匹配。
6、 根据权利要求 4所述的调节器结构， 其特征在于， 所述凹槽有内螺紋；
所述调节器滑动件为螺杆， 所述凹槽的内螺紋与所述调节器滑动件的外螺紋啮合固定。
7、 根据权利要求 1至 3任一项所述的调节器结构， 其特征在于， 所述支撑件的外周设置 密封槽； 在所述密封槽内设置密封圏。
8、 根据权利要求 1所述的调节器结构， 其特征在于， 所述调节器的长度大于所述支撑件 的长度。
9、 一种离心式压缩机， 包括叶轮， 其特征在于， 还包括权利要求 1至 8任一项所述的调 节器结构。
10、 根据权利要求 9所述的离心式压缩机， 其特征在于， 所述调节器结构的调节器的外 螺紋端置于所述叶轮的出口处；
所述电机驱动所述主动齿轮正向旋转时， 带动所述从动齿轮正向旋转， 所述调节器的外 螺紋端持续回缩， 直至所述叶轮出口完全打开； 所述电机驱动所述主动齿轮反向旋转时， 带 动所述从动齿轮反向旋转， 所述调节器向所述外螺紋端持续伸出， 直至所述叶轮出口完全封 闭。
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