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WO2019061898A1 - 泵体组件、流体机械及换热设备 - Google Patents

泵体组件、流体机械及换热设备 Download PDF

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Publication number
WO2019061898A1
WO2019061898A1 PCT/CN2017/118331 CN2017118331W WO2019061898A1 WO 2019061898 A1 WO2019061898 A1 WO 2019061898A1 CN 2017118331 W CN2017118331 W CN 2017118331W WO 2019061898 A1 WO2019061898 A1 WO 2019061898A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump body
body assembly
sliding
slider
fixing bracket
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.)
Ceased
Application number
PCT/CN2017/118331
Other languages
English (en)
French (fr)
Inventor
邓丽颖
杨国蟒
梁社兵
万鹏凯
徐嘉
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Original Assignee
Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
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 Gree Green Refrigeration Technology Center Co Ltd of Zhuhai filed Critical Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Publication of WO2019061898A1 publication Critical patent/WO2019061898A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • 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

Definitions

  • the invention relates to the technical field of compressors, in particular to a pump body assembly, a fluid machine and a heat exchange device.
  • the rotary compressor has a larger stroke of the slider.
  • the slide spring is prone to bending and deformation, causing the head of the slide to be disengaged from the inner wall of the cylinder, and the tail of the slide hits the slide groove, and the slide is prone to occur after being extended again.
  • the above phenomenon easily causes the sliding piece to disengage from the cylinder, causing an impact between the sliding piece, the cylinder and the sliding groove, resulting in damage to the internal structure of the compressor and shortening the service life of the compressor.
  • the above situation tends to cause the sealing of each chamber in the cylinder to be reduced, and the gas compression is insufficient, which seriously affects the working performance of the compressor.
  • the main object of the present invention is to provide a pump body assembly, a fluid machine, and a heat exchange device to solve the problem that the slider and the cylinder of the pump body assembly are easily detached.
  • a pump body assembly includes: a rotating shaft having a rotor portion, and a plurality of sliding vanes are disposed on the rotor portion; the cylinder, the rotating shaft is disposed in the cylinder, and The cylinder has an inner cavity; a plurality of sliding pieces, a plurality of sliding pieces are slidably disposed in each sliding groove, the head of the sliding piece is in contact with the cavity wall of the inner cavity; and a plurality of sliding piece springs are disposed on each sliding piece
  • the sliding spring is located in the tail of each sliding piece; a plurality of guiding structures are disposed in each sliding slot, and the guiding structure protrudes in the moving direction of the sliding piece, and the sliding spring is sleeved on the guiding structure.
  • a sliding plate hole is disposed on an end surface of the sliding piece adjacent to the sliding spring, and the guiding structure extends into the sliding hole.
  • the pump body assembly further includes a fixing bracket, and the guiding structure is fixed in the sliding slot by the fixing bracket.
  • a slot structure is arranged on the slot wall of the sliding slot, and the fixing bracket is clamped in the limiting structure to prevent the fixed bracket from moving relative to the sliding slot.
  • the fixing bracket has a plate shape, and the guiding structure is perpendicular to the plate-shaped fixing bracket.
  • the fixing bracket is an I-shaped structure.
  • the end of the fixing bracket has a locking protrusion
  • the end surface of the rotor portion along the axial direction of the rotating shaft is provided with a finite recess
  • the engaging protrusion is embedded in the limiting recess
  • the depth H1 and the card of the limiting recess The heights H2 of the joints are equal.
  • the fixing bracket includes two sub-brackets, and the ends of the two sub-frames away from each other have the engaging protrusions, and each of the sub-brackets is provided with a guiding structure.
  • the guiding structure comprises: a boss structure disposed at an end of the guiding structure near the fixing bracket, and the boss structure can cooperate with the sliding spring stop.
  • the limiting structure is a limiting slot formed on the slot wall of the sliding slot.
  • the two groove walls of the opposite arrangement of the sliding groove are provided with a finite structure, and the connecting line L1 of the two limiting structures is perpendicular to the moving direction of the sliding piece.
  • the slot width W of the slider slot the distance W1 between the two limiting structures, where W ⁇ W1.
  • two or more slider holes are disposed on the slider.
  • the guiding structure is a columnar structure, and the difference between the inner diameter D1 of the vane spring and the radial dimension D3 of the guiding structure is ⁇ D1, wherein 0.01 mm ⁇ D1 ⁇ 0.03 mm.
  • the slider hole includes a first hole segment and a second hole segment which are sequentially connected, the guiding structure extends into the first hole segment, and the difference between the diameter D4 of the first hole segment and the radial dimension D3 of the guiding structure Is ⁇ D2, where 0.01mm ⁇ D2 ⁇ 0.03mm; the aperture D5 of the second hole segment is smaller than the aperture D4 of the first hole segment, and the difference between the aperture D5 of the second hole segment and the outer diameter D2 of the vane spring is ⁇ D3, Wherein, 0.01 mm ⁇ ⁇ D3 ⁇ 0.03 mm.
  • the distance between the guide structure and the tail vane is X1
  • the distance between the guide structure and the tail vane is X1
  • the distance between the guide structure and the tail vane is X1
  • the distance between the guide structure and the tail vane is X1
  • the distance between the guide structure and the tail vane is X1
  • the distance between the guide structure and the tail vane is X1
  • the slide extends into the lumen of the maximum length
  • the length of the slider spring is L max
  • the depth of the first hole segment is X2
  • the depth of the second hole segment is X3
  • the length of the guiding structure is X4
  • the fixing bracket is provided with a plurality of guiding structures, and the plurality of guiding structures are spaced apart along the vertical extending direction of the fixing bracket.
  • a fluid machine including the pump body assembly described above.
  • a heat exchange apparatus comprising the fluid machine described above.
  • the pump body assembly includes a rotating shaft, a cylinder, a plurality of sliding sheets, a plurality of sliding springs and a plurality of guiding structures.
  • the rotating shaft has a rotor portion, and the rotor portion is provided with a plurality of sliding vanes.
  • the rotating shaft is bored in the cylinder, and the cylinder has an inner cavity.
  • a plurality of sliding sheets are slidably disposed in the respective sliding groove, and the head of the sliding piece is in contact with the cavity wall of the inner cavity.
  • a plurality of vane springs are disposed in each of the vane slots, and each vane spring is located at a tail portion of each of the vanes.
  • a plurality of guiding structures are disposed in each of the sliding slot, and the guiding structure protrudes in a moving direction of the sliding piece, and the sliding spring is sleeved on the guiding structure.
  • the vane spring is sleeved on the guiding structure to guide the vane spring, and the vane spring does not undergo bending deformation, and the head of the sliding vane can always be ensured with the inner cavity.
  • the walls of the chamber are in contact so that the vanes are placed against the cylinder.
  • the sliding piece of the pump body assembly of the present application and the cavity wall of the inner cavity are always in close contact with each other, and the phenomenon that the tail portion of the sliding piece hits the sliding piece groove or the head of the sliding piece hits the cylinder occurs, thereby extending the sliding piece,
  • the service life of the cylinder and the shaft reduces the vibration and noise generated during the operation of the pump body assembly.
  • the pump body assembly of the present application can ensure the sealing of each chamber of the cylinder and improve the working performance of the pump body assembly.
  • Figure 1 shows a front view of a first embodiment of a pump body assembly according to the present invention
  • Figure 2 is a cross-sectional view taken along line A-A of the pump body assembly of Figure 1;
  • Figure 3 is a front elevational view showing the rotating shaft of the pump body assembly of Figure 1;
  • Figure 4 is a cross-sectional view taken along the line B-B of the rotating shaft of Figure 3;
  • Figure 5 is a perspective view showing the assembled structure of the slider spring, the guiding structure and the fixing bracket of Figure 1;
  • Figure 6 is a perspective view showing the guide structure and the fixing bracket of Figure 1;
  • Figure 7 shows a cross-sectional view of the slider of Figure 1;
  • Figure 8 is a partial structural view showing the head of the slide body of the pump body assembly of Figure 1 when it is completely positioned in the slide groove;
  • Figure 9 is a partial structural view showing the length of the sliding piece of the pump body assembly of Figure 1 extending into the inner cavity;
  • Figure 10 is a front elevational view of the slider spring of Figure 1;
  • Figure 11 is a perspective view showing the guide structure and the fixing bracket of the second embodiment of the pump body assembly according to the present invention.
  • Figure 12 is a perspective view showing the guide structure and the fixing bracket of the third embodiment of the pump body assembly according to the present invention.
  • Figure 13 is a perspective view showing the guide structure and the fixing bracket of the fourth embodiment of the pump body assembly according to the present invention.
  • Figure 14 is a front elevational view showing the rotating shaft of the pump body assembly of the fourth embodiment of the pump body assembly according to the present invention.
  • Fig. 15 is a cross-sectional view taken along line C-C of the rotating shaft of Fig. 14.
  • orientation words used such as “up and down”, are generally referred to in the directions shown in the drawings, or in the vertical, vertical or gravity directions, without being otherwise described.
  • “left and right” are generally for the left and right as shown in the drawing; “inside and outside” refer to the inside and outside of the contour of each component, but the above orientation Words are not intended to limit the invention.
  • the present application provides a pump body assembly, a fluid machine and a heat exchange device.
  • the pump body assembly includes a rotating shaft 10, a cylinder 20, a plurality of sliding sheets 30, a plurality of vane springs 40, and a plurality of guiding structures 50.
  • the rotating shaft 10 has a rotor portion 11, and the rotor portion 11 is provided with a plurality of slider grooves 111.
  • the rotating shaft 10 is bored in the cylinder 20, and the cylinder 20 has a cavity 21.
  • a plurality of sliders 30 are slidably disposed in the respective slider grooves 111, and the heads of the sliders 30 are in contact with the cavity walls of the inner chamber 21.
  • a plurality of vane springs 40 are disposed in each of the vane slots 111, and each vane spring 40 is located at the tail of each of the vanes 30.
  • a plurality of guiding structures 50 are disposed in each of the sliding groove 111, and the guiding structure 50 projects in the moving direction of the sliding piece 30, and the sliding spring 40 is sleeved on the guiding structure 50.
  • the vane spring 40 is sleeved on the guiding structure 50 to guide the vane spring 40, and the vane spring 40 does not undergo bending deformation, and the head of the sliding vane 30 can be ensured.
  • the chamber wall of the inner chamber 21 is always in contact such that the slider 30 is placed against the cylinder 20.
  • the sliding plate 30 of the pump body assembly of the present embodiment and the cavity wall of the inner cavity 21 are always in close contact with each other, so that the tail portion of the sliding plate 30 can be prevented from colliding with the sliding plate groove 111 or the head of the sliding plate 30 hits the cylinder 20.
  • the pump body assembly of the present embodiment can ensure the sealing of the respective chambers of the cylinder 20 and improve the working performance of the pump body assembly.
  • the end surface of the slider 30 adjacent to the slider spring 40 is provided with a slider hole 31, and the guiding structure 50 projects into the slider hole 31.
  • the vane spring 40 and the guiding structure 50 always extend into the vane hole 31, so that the vane spring 40 does not always undergo bending deformation in the vane slot 111, and The effective support of the slider spring 40 to the tail of the slider 30 is achieved, and the vane spring 40 is compressed along the direction of movement of the slider 30, thereby ensuring that the head of the slider 30 is always in contact with the inner wall of the cylinder 20 and There is no impact with the cylinder 20.
  • the above structure has a simple structure, is easy to assemble, and can ensure the motion reliability of the guide structure 50.
  • the pump body assembly further includes a fixing bracket 60, and the guiding structure 50 is fixed in the slider groove 111 by the fixing bracket 60.
  • the guiding structure 50 is disposed on the fixing bracket 60, and the fixing bracket 60 and the sliding slot 111 are fixed to fix the guiding structure 50 and the sliding slot 111.
  • the structure described above is simple in structure and easy to implement.
  • the fixing bracket 60 is easy to process and has less influence on the structural strength of the rotating shaft 10, thereby prolonging the service life of the pump body assembly.
  • the fixing manner of the guiding structure 50 is not limited thereto, as long as the guiding structure 50 can be prevented from moving relative to the sliding slot 111.
  • the guide structure 50 is threaded or welded to the vane slot 111.
  • a slot structure 111a is disposed on the slot wall of the slider slot 111, and the fixing bracket 60 is locked in the limiting structure 111a to prevent the fixing bracket 60 from moving relative to the slider slot 111.
  • the limiting structure 111a is engaged with the fixing bracket 60, and the fixing of the fixing bracket 60 and the sliding slot 111 is facilitated, that is, the guiding structure 50 and the sliding slot 111 are fixed.
  • the engagement of the fixing bracket 60 with the limiting structure 111a makes the installation or disassembly between the two easier and more convenient.
  • the fixing manner of the fixing bracket 60 and the limiting structure 111a is not limited thereto.
  • the fixing bracket 60 is connected to the limiting structure 111a by a fastener or welded or riveted.
  • the fixing bracket 60 has a plate shape, and the guiding structure 50 is perpendicular to the plate-shaped fixing bracket 60.
  • the above structure has a simple structure and is easy to process.
  • the above arrangement also makes the processing of the limiting structure 111a easier, that is, in the same sliding groove 111, the two groove walls of the opposite arrangement of the sliding groove 111 are provided with the limiting structure 111a, and the two limiting structures 111a
  • the wire L1 is disposed perpendicular to the moving direction of the slider 30.
  • the fixing bracket 60 is locked in the limiting structure 111a, so that the extending direction of the guiding structure 50 is along the moving direction of the sliding piece 30, thereby preventing the sliding spring 40 from being deformed in other directions, and ensuring the normal operation of the pump body assembly.
  • angle between the guiding structure 50 and the fixing bracket 60 is not limited thereto, as long as the guiding structure 50 can be disposed along the moving direction of the sliding sheet 30.
  • the limiting structure 111a is a limiting slot formed on the groove wall of the sliding slot 111.
  • the limit groove has a simple structure and is easy to process, thereby reducing the processing cost of the pump body assembly and reducing the labor intensity of the worker.
  • the limiting slot is a rectangular slot.
  • the rectangular groove has a simple structure and is easy to process.
  • the shape of the groove cross section of the limiting groove is not limited thereto.
  • the limiting slot is an arcuate slot.
  • two or more slider holes 31 are disposed on the slider 30.
  • the slider 30 is provided with two slider holes 31 , and the two slider holes 31 are respectively located on two sides of the horizontal plane where the geometric center of the slider 30 is located. And the two slider holes 31 are symmetrically arranged along the horizontal plane. In this way, the above arrangement can ensure that the force of the sliding piece 30 is more uniform, and the movement of the sliding piece 30 is more stable, the working performance of the pump body assembly is improved, the vibration and noise generated during the starting or running of the pump body assembly are reduced, and the user is improved. Use experience.
  • the position at which the slider hole 31 is disposed is not limited thereto.
  • the selection and arrangement of the slider spring 40 is such that the slider 30 is subjected to force balance and torque balance.
  • the guide structure 50 is a columnar structure, and the difference between the inner diameter D1 of the vane spring 40 and the radial dimension D3 of the guide structure 50 is ⁇ D1, where 0.01 mm ⁇ ⁇ D1 ⁇ 0.03 mm.
  • the above-mentioned arrangement ensures that the vane spring 40 can be sleeved outside the guide structure 50, and on the other hand, the gap between the two can be prevented from being excessively large, resulting in a significant sway of the vane spring 40 during operation of the pump body assembly. In this way, the above numerical range can ensure the smooth operation of the pump body assembly, thereby improving the working performance of the pump body assembly.
  • the slider hole 31 includes a first hole segment 311 and a second hole segment 312 which are sequentially connected, the guiding structure 50 extends into the first hole segment 311, and the aperture D4 of the first hole segment 311 is
  • the difference between the radial dimension D3 of the guiding structure 50 is ⁇ D2, wherein 0.01mm ⁇ D2 ⁇ 0.03mm; the aperture D5 of the second hole segment 312 is smaller than the aperture D4 of the first hole segment 311, and the aperture D5 of the second hole segment 312
  • the difference from the outer diameter D2 of the vane spring 40 is ⁇ D3, where 0.01 mm ⁇ ⁇ D3 ⁇ 0.03 mm.
  • the above arrangement can ensure that one end of the guiding structure 50 is stopped at the stepped surface of the first hole section 311 and the second hole section 312, and the other end of the guiding structure 50 is fixed in the sliding groove 111, thereby preventing the guiding structure.
  • the sloshing occurs, so that the vane spring 40 can smoothly slide on the guiding structure 50, thereby improving the operational reliability of the guiding structure 50, preventing the vane spring 40 from being deformed in other directions, and causing the head and the cylinder of the sliding vane 30. 20 detached.
  • the length of the slider spring 40 is Lmin
  • the distance between the tail portion of the slider 30 and the guiding structure 50 is X1.
  • the length of the sliding piece 30 extending into the inner cavity 21 is the largest
  • the length of the sliding spring 40 is L max
  • the depth of the first hole segment 311 is X2
  • the depth of the second hole segment 312 is X3
  • the length of the guiding structure 50 It is X4
  • the above arrangement not only ensures that the guide structure 50 is always disposed in the first hole section 311, and ensures that the slide spring 40 does not excessively be compressed to affect its structural strength.
  • the above numerical relationship can ensure that the slide spring 30 is still in a micro-compressed state when the length of the slide 30 extends into the inner cavity 21 is maximum, and the head of the slide 30 does not disengage from the cylinder 20, thereby avoiding the pump assembly. The slide 30 is disengaged from the cylinder 20 during operation causing the tail or head of the slider 30 to strike the cylinder 20.
  • the original length of the vane spring 40 is L 0
  • the vane spring 40 is in a state of maximum deformation
  • the length of the vane spring 40 is L min .
  • the slider spring 40 is in a micro-compressed state
  • the length of the slider spring 40 is its maximum length L max
  • the slider 30 is still provided with an elastic force in accordance with the direction of the centrifugal force, and is slippery.
  • the leaf spring 40 is in full contact with the slider 30 to prevent the tail portion of the slider 30 from striking the slider groove 111.
  • L min ⁇ L max ⁇ L 0 is satisfied.
  • the maximum pressure difference experienced by the slider 30 is F
  • the number of the slider springs 40 used by the single slider 30 is n.
  • the two slider holes 31 are symmetrically disposed along the neutral layer of the slider 30, that is, the distance X5 and the distance X6 between the two slider holes 31 and the neutral layer are equal.
  • the fixing bracket 60 is provided with a plurality of guiding structures 50, and the plurality of guiding structures 50 are spaced apart along the vertical extending direction of the fixing bracket 60.
  • two fixing structures 50 are disposed on the fixing bracket 60
  • two guiding structures 50 are spaced apart along the vertical extending direction of the fixing bracket 60
  • the two guiding structures 50 and The two slider holes 31 are provided in one-to-one correspondence.
  • the above structure can ensure the structural stability of the fixing bracket 60 and prolong the service life of the fixing bracket 60.
  • the pump body assembly further includes an upper flange 71 and a lower flange 72.
  • the rotating shaft 10 is disposed in the upper flange 71 and the lower flange 72, and the cylinder 20 is disposed between the upper flange 71 and the lower flange 72.
  • the sliding piece 30 protrudes from the sliding groove 111 under the action of centrifugal force, back pressure and elastic force, and starts a reciprocating straight line in the sliding groove 111. Movement, the head of the slider 30 is in contact with the inner wall surface of the cylinder 20.
  • the three sliding sheets 30 and the inner wall surface of the cylinder 20 and the upper flange 71 and the lower flange 72 divide the entire crescent cavity of the cylinder 20 into three independent chambers, and the three chambers are periodically enlarged and contracted to realize the pump. Intake, compression and exhaust of the body components.
  • the present application also provides a fluid machine (not shown) including the pump body assembly described above.
  • the fluid machine is a compressor.
  • the application also provides a heat exchange device (not shown) including the fluid machine described above.
  • the heat exchange device is an air conditioner.
  • the pump assembly of the second embodiment differs from the first embodiment in that the structure of the fixing bracket 60 is different.
  • the fixing bracket 60 has an I-shaped structure.
  • the above arrangement can reduce the weight of the fixing bracket 60, make the pump body assembly more lightweight, and improve the working efficiency and working performance of the pump body assembly.
  • the fixing bracket 60 is provided with a weight reducing hole, and the weight reducing hole avoiding guiding structure 50 is disposed.
  • the pump body assembly of the third embodiment differs from the first embodiment in that the structure of the guide structure 50 is different.
  • the guide structure 50 includes a boss structure 51.
  • the boss structure 51 is disposed at one end of the guiding structure 50 near the fixing bracket 60, and the boss structure 51 can be engaged with the sliding spring 40.
  • the boss structure 51 can limit the stop of the slide spring 40, and the elastic deformation amount of the slide spring 40 can be increased, and the worker can appropriately select the length of the slide spring 40 as needed.
  • the boss structure 51 has a simple structure and is easy to process.
  • the pump body assembly of the fourth embodiment differs from the first embodiment in that the structure of the fixing bracket 60 is different.
  • the fixing bracket 60 includes two sub-brackets 62 , and one end of the two sub-frames 62 away from each other has a locking protrusion 61 , and each of the sub-frames 62 is provided with a guiding structure 50 .
  • the above arrangement can further reduce the weight of the fixing bracket 60 and realize the lightweight design of the fixing bracket 60.
  • the groove width W of the slider groove 111 and the distance W1 between the two stopper structures 111a where W ⁇ W1.
  • the end portion of the fixing bracket 60 has a catching projection 61.
  • the end surface of the rotor portion 11 along the axial direction of the rotating shaft 10 is provided with a finite recess 12, and the engaging projection 61 is embedded in the limiting recess 12.
  • the depth H1 of the limiting recess 12 is equal to the height H2 of the engaging projection 61.
  • the vane spring is sleeved on the guiding structure to guide the vane spring, and the vane spring does not undergo bending deformation, and the head of the sliding vane can always be ensured with the inner cavity.
  • the walls of the chamber are in contact so that the vanes are placed against the cylinder.
  • the sliding piece of the pump body assembly of the present application and the cavity wall of the inner cavity are always in close contact with each other, and the phenomenon that the tail portion of the sliding piece hits the sliding piece groove or the head of the sliding piece hits the cylinder occurs, thereby extending the sliding piece,
  • the service life of the cylinder and the shaft reduces the vibration and noise generated during the operation of the pump body assembly.
  • the pump body assembly of the present application can ensure the sealing of each chamber of the cylinder and improve the working performance of the pump body assembly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

一种泵体组件，包括：转轴（10），具有转子部（11），且转子部（11）上设置有多个滑片槽（111）；气缸（20），转轴（10）穿设在气缸（20）内，且气缸（20）具有内腔（21）；多个滑片（30），多个滑片（30）可滑动地设置在各滑片槽（111）内，滑片（30）的头部与内腔（21）的腔壁相接触；多个滑片弹簧（40），设置在各滑片槽（111）内，且各滑片弹簧（40）位于各滑片（30）的尾部；多个导向结构（50），设置在各滑片槽（111）内，且导向结构（50）沿滑片（30）的运动方向伸出，滑片弹簧（40）套设在导向结构（50）上。还提供了具有上述泵体组件的流体机械和换热设备。采用上述结构，能够防止泵体组件的滑片（30）与气缸（20）发生脱离，进而延长滑片（30）、气缸（20）及转轴（10）的使用寿命。

Description

泵体组件、流体机械及换热设备 技术领域
本发明涉及压缩机技术领域，具体而言，涉及一种泵体组件、流体机械及换热设备。
背景技术
在现有技术中，旋转式压缩机的滑片行程较大。在压缩机启动或运行过程中，滑片弹簧易发生折弯变形，导致滑片的头部脱离气缸的内腔壁，且滑片的尾部撞击滑片槽，滑片再次伸出后极易发生滑片的头部撞击气缸的情况。这样，上述现象易导致滑片与气缸脱离，造成滑片、气缸及滑片槽之间发生撞击而导致压缩机内部结构的损坏，缩短了压缩机的使用寿命。同时，上述情况易导致气缸内的各个腔室密封性降低，气体压缩不充分，严重影响了压缩机的工作性能。
发明内容
本发明的主要目的在于提供一种泵体组件、流体机械及换热设备，以解决现有技术中泵体组件的滑片与气缸易发生脱离的问题。
为了实现上述目的，根据本发明的一个方面，提供了一种泵体组件，包括：转轴，具有转子部，且转子部上设置有多个滑片槽；气缸，转轴穿设在气缸内，且气缸具有内腔；多个滑片，多个滑片可滑动地设置在各滑片槽内，滑片的头部与内腔的腔壁相接触；多个滑片弹簧，设置在各滑片槽内，且各滑片弹簧位于各滑片的尾部；多个导向结构，设置在各滑片槽内，且导向结构沿滑片的运动方向伸出，滑片弹簧套设在导向结构上。
进一步地，滑片的靠近滑片弹簧的端面上设置有滑片孔，且导向结构伸入至滑片孔内。
进一步地，泵体组件还包括固定支架，导向结构通过固定支架固定在滑片槽内。
进一步地，滑片槽的槽壁上设置有限位结构，固定支架卡设在限位结构内，以防止固定支架相对于滑片槽发生运动。
进一步地，固定支架呈板状，且导向结构垂直于呈板状的固定支架。
进一步地，固定支架为工字型结构。
进一步地，固定支架的端部具有卡接凸起，转子部的沿转轴的轴向方向的端面上设置有限位凹部，卡接凸起嵌入限位凹部内，且限位凹部的深度H1与卡接凸起的高度H2相等。
进一步地，固定支架包括两个子支架，且两个子支架彼此远离的一端均具有卡接凸起，各子支架上均设置有一个导向结构。
进一步地，导向结构包括：凸台结构，设置在导向结构的靠近固定支架的一端，且凸台结构能够与滑片弹簧止挡配合。
进一步地，限位结构为开设在滑片槽的槽壁上的限位槽。
进一步地，同一个滑片槽内，滑片槽的相对设置的两个槽壁上均设置有限位结构，且两个限位结构的连线L1与滑片的运动方向垂直设置。
进一步地，滑片槽的槽宽W，两个限位结构之间的距离W1，其中，W≤W1。
进一步地，滑片上设置有两个或者多个滑片孔。
进一步地，导向结构为柱状结构，滑片弹簧的内径D1与导向结构的径向尺寸D3之差为ΔD1，其中，0.01mm≤ΔD1≤0.03mm。
进一步地，滑片孔包括顺次连接的第一孔段和第二孔段，导向结构伸入至第一孔段内，且第一孔段的孔径D4与导向结构的径向尺寸D3之差为ΔD2，其中，0.01mm≤ΔD2≤0.03mm；第二孔段的孔径D5小于第一孔段的孔径D4，且第二孔段的孔径D5与滑片弹簧的外径D2之差为ΔD3，其中，0.01mm≤ΔD3≤0.03mm。
进一步地，当滑片的头部完全位于滑片槽内时，滑片弹簧的长度为L min，滑片的尾部与导向结构之间的距离为X1，当滑片伸入内腔的长度最大时，滑片弹簧的长度为L max，第一孔段的深度为X2，第二孔段的深度为X3，导向结构的长度为X4，且滑片弹簧的线径D0，其中，D0＝(D2-D1)/2，则满足关系：L max-4D0≤X4≤X1+X2+X3。
进一步地，固定支架上设置有多个导向结构，且多个导向结构沿固定支架的竖直延伸方向上间隔设置。
根据本发明的另一方面，提供了一种流体机械，包括上述的泵体组件。
根据本发明的另一方面，提供了一种换热设备，包括上述的流体机械。
应用本发明的技术方案，泵体组件包括转轴、气缸、多个滑片、多个滑片弹簧及多个导向结构。其中，转轴具有转子部，且转子部上设置有多个滑片槽。转轴穿设在气缸内，且气缸具有内腔。多个滑片可滑动地设置在各滑片槽内，滑片的头部与内腔的腔壁相接触。多个滑片弹簧设置在各滑片槽内，且各滑片弹簧位于各滑片的尾部。多个导向结构设置在各滑片槽内，且导向结构沿滑片的运动方向伸出，滑片弹簧套设在导向结构上。
在泵体组件启动或者运行过程中，滑片弹簧套设在导向结构上以对滑片弹簧进行导向，则滑片弹簧不会发生折弯变形，能够保证滑片的头部始终与内腔的腔壁相接触，使得滑片紧贴气缸设置。这样，本申请中的泵体组件的滑片与内腔的腔壁始终紧贴设置，能够避免滑片的尾部撞击滑片槽或者滑片的头部撞击气缸的现象发生，进而延长滑片、气缸及转轴的使用寿命，减小泵体组件运行过程中产生的振动和噪声。此外，本申请中的泵体组件能够保证气缸的各个腔室的密封性，提升泵体组件的工作性能。
附图说明
构成本申请的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：
图1示出了根据本发明的泵体组件的实施例一的主视图；
图2示出了图1中的泵体组件的A-A向剖视图；
图3示出了图1中的泵体组件的转轴的主视图；
图4示出了图3中的转轴的B-B向剖视图；
图5示出了图1中的滑片弹簧、导向结构及固定支架装配后的立体结构示意图；
图6示出了图1中的导向结构及固定支架的立体结构示意图；
图7示出了图1中的滑片的剖视图；
图8示出了图1中的泵体组件的滑片的头部完全位于滑片槽内时的局部结构图；
图9示出了图1中的泵体组件的滑片伸入内腔的长度最大时的局部结构图；
图10示出了图1中的滑片弹簧的主视图；
图11示出了根据本发明的泵体组件的实施例二的导向结构及固定支架的立体结构示意图；
图12示出了根据本发明的泵体组件的实施例三的导向结构及固定支架的立体结构示意图；
图13示出了根据本发明的泵体组件的实施例四的导向结构及固定支架的立体结构示意图；
图14示出了根据本发明的泵体组件的实施例四的泵体组件的转轴的主视图；以及
图15示出了图14中的转轴的C-C向剖视图。
其中，上述附图包括以下附图标记：
10、转轴；11、转子部；111、滑片槽；111a、限位结构；12、限位凹部；20、气缸；21、内腔；30、滑片；31、滑片孔；311、第一孔段；312、第二孔段；40、滑片弹簧；50、导向结构；51、凸台结构；60、固定支架；61、卡接凸起；62、子支架；71、上法兰；72、下法兰。
具体实施方式
需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本发明。
需要指出的是，除非另有指明，本申请使用的所有技术和科学术语具有与本申请所属技术领域的普通技术人员通常理解的相同含义。
在本发明中，在未作相反说明的情况下，使用的方位词如“上、下”通常是针对附图所示的方向而言的，或者是针对竖直、垂直或重力方向上而言的；同样地，为便于理解和描述，“左、右”通常是针对附图所示的左、右；“内、外”是指相对于各部件本身的轮廓的内、外，但上述方位词并不用于限制本发明。
为了解决现有技术中泵体组件的滑片与气缸易发生脱离的问题，本申请提供了一种泵体组件、流体机械及换热设备。
实施例一
如图1和图2所示，泵体组件包括转轴10、气缸20、多个滑片30、多个滑片弹簧40及多个导向结构50。其中，转轴10具有转子部11，且转子部11上设置有多个滑片槽111。转轴10穿设在气缸20内，且气缸20具有内腔21。多个滑片30可滑动地设置在各滑片槽111内，滑片30的头部与内腔21的腔壁相接触。多个滑片弹簧40设置在各滑片槽111内，且各滑片弹簧40位于各滑片30的尾部。多个导向结构50设置在各滑片槽111内，且导向结构50沿滑片30的运动方向伸出，滑片弹簧40套设在导向结构50上。
在泵体组件启动或者运行过程中，滑片弹簧40套设在导向结构50上以对滑片弹簧40进行导向，则滑片弹簧40不会发生折弯变形，能够保证滑片30的头部始终与内腔21的腔壁相接触，使得滑片30紧贴气缸20设置。这样，本实施例中的泵体组件的滑片30与内腔21的腔壁始终紧贴设置，能够避免滑片30的尾部撞击滑片槽111或者滑片30的头部撞击气缸20的现象发生，进而延长滑片30、气缸20及转轴10的使用寿命，减小泵体组件运行过程中产生的振动和噪声。此外，本实施例中的泵体组件能够保证气缸20的各个腔室的密封性，提升泵体组件的工作性能。
如图7所示，滑片30的靠近滑片弹簧40的端面上设置有滑片孔31，且导向结构50伸入至滑片孔31内。这样，在泵体组件启动或者运行过程中，滑片弹簧40及导向结构50始终伸入至滑片孔31内，使得滑片弹簧40在滑片槽111内始终不会发生折弯变形，且实现了滑片弹簧40对滑片30的尾部的有效支撑，滑片弹簧40沿着滑片30的运动方向被压缩，进而保证滑片30的头部始终与气缸20的内腔壁相接触且不会与气缸20发生撞击。上述结构的结构简单，容易装配，且能够保证导向结构50的运动可靠性。
如图5、图6、图8及图9所示，泵体组件还包括固定支架60，导向结构50通过固定支架60固定在滑片槽111内。这样，导向结构50设置在固定支架60上，将固定支架60与滑片槽111固定即可实现导向结构50与滑片槽111的固定。上述结构的结构简单，容易实现。此外，固定支架60容易加工，且对转轴10的结构强度影响较小，进而延长泵体组件的使用寿命。
需要说明的是，导向结构50的固定方式不限于此，只要能够保证导向结构50不会相对于滑片槽111发生运动即可。可选地，导向结构50与滑片槽111螺纹连接或者焊接。
如图3和图4所示，滑片槽111的槽壁上设置有限位结构111a，固定支架60卡设在限位结构111a内，以防止固定支架60相对于滑片槽111发生运动。具体地，限位结构111a与固定支架60卡接，易实现固定支架60与滑片槽111的固定，即实现导向结构50与滑片槽111的固定。这样，固定支架60与限位结构111a的卡接使得二者之间的安装或者拆卸更加容易、方便。
需要说明的是，固定支架60与限位结构111a的固定方式不限于此。可选地，固定支架60与限位结构111a通过紧固件连接或者焊接或者铆接。
如图5和图6所示，固定支架60呈板状，且导向结构50垂直于呈板状的固定支架60。这样，上述结构的结构简单，容易加工。上述设置也使得限位结构111a的加工更加容易，即同一个滑片槽111内，滑片槽111的相对设置的两个槽壁上均设置有限位结构111a，且两个限位结构111a的连线L1与滑片30的运动方向垂直设置。这样，固定支架60卡设在限位结构111a内，使得导向结构50的延伸方向沿滑片30的运动方向，进而防止滑片弹簧40发生其他方向的变形，保证泵体组件的正常运行。
需要说明的是，导向结构50与固定支架60之间的夹角设置不限于此，只要能够导向结构50沿滑片30的运动方向设置即可。
如图3和图4所示，限位结构111a为开设在滑片槽111的槽壁上的限位槽。限位槽的结构简单，容易加工，进而降低泵体组件的加工成本，降低工作人员的劳动强度。
可选地，限位槽为矩形槽。矩形槽的结构简单，容易加工。
需要说明的是，限位槽的槽截面形状不限于此。可选地，限位槽为弧形槽。
可选地，滑片30上设置有两个或者多个滑片孔31。如图2和图7所示，在本实施例中，滑片30上设置有两个滑片孔31，且两个滑片孔31分别位于滑片30的几何中心所在的水平面的两侧，且两个滑片孔31沿该水平面对称设置。这样，上述设置能够保证滑片30的受力更加均匀，则滑片30的运动更加平稳，提高了泵体组件的工作性能，降低泵体组件启动或者运行过程中产生的振动和噪声，提高用户使用体验。
需要说明的是，滑片孔31的设置位置不限于此。当滑片30的重心下移或上移时，则滑片弹簧40的选择及布置要保证滑片30受力平衡及力矩平衡。
如图6和图10所示，导向结构50为柱状结构，滑片弹簧40的内径D1与导向结构50的径向尺寸D3之差为ΔD1，其中，0.01mm≤ΔD1≤0.03mm。上述设置一方面保证滑片弹簧40能够套设在导向结构50外，另一方面使得二者之间的间隙不会过大而导致滑片弹簧40在泵体组件运行过程中发生明显的晃动。这样，上述数值范围能够保证泵体组件的平稳运行，进而提升了泵体组件的工作性能。
如图7所示，滑片孔31包括顺次连接的第一孔段311和第二孔段312，导向结构50伸入至第一孔段311内，且第一孔段311的孔径D4与导向结构50的径向尺寸D3之差为ΔD2，其中，0.01mm≤ΔD2≤0.03mm；第二孔段312的孔径D5小于第一孔段311的孔径D4，且第二孔段312的孔径D5与滑片弹簧40的外径D2之差为ΔD3，其中，0.01mm≤ΔD3≤0.03mm。这样，上述设置能够保证导向结构50的一端被止挡在第一孔段311与第二孔段312的台阶面处，导向结构50的另一端被固定在滑片槽111内，进而防止导向结构50发生晃动，使得滑片弹簧40能够在导向结构50上平稳地滑动，进而提高导向结构50的工作可靠性，防止滑片弹簧40发生其他方向上的变形而导致滑片30的头部与气缸20脱离。
如图8和图9所示，当滑片30的头部完全位于滑片槽111内时，滑片弹簧40的长度为L min，滑片30的尾部与导向结构50之间的距离为X1，当滑片30伸入内腔21的长度最大时，滑片弹簧40的长度为L max，第一孔段311的深度为X2，第二孔段312的深度为X3，导向结构50的长度为X4，且滑片弹簧40的线径D0，其中，D0＝(D2-D1)/2，则满足关系：L max-4D0≤X4≤X1+X2+X3。这样，上述设置不仅能够保证导向结构50始终设置在第一孔段311内，且保证滑片弹簧40不会发生过度被压缩而影响其结构强度。此外，上述数值关系能够保证滑片30伸入内腔21的长度最大时，滑片弹簧40仍处于微压缩状态，则滑片30的头部不会与气缸20发生脱离，可避免泵体组件运行过程中滑片30脱离气缸20而导致滑片30的尾部或头部撞击气缸20。
具体地，在本实施例中，滑片弹簧40的原始长度为L 0，当滑片30的伸出量最小时，滑片弹簧40处于变形最大的状态，此时滑片弹簧40的长度为L min。当滑片30的伸出量最大时，滑片弹簧40处于微压缩状态，此时滑片弹簧40的长度为其最大长度L max，仍对滑片30提供与离心力方向一致的弹性力，滑片弹簧40与滑片30全程接触，可避免滑片30的尾部撞击滑片槽111。且满足L min≤L max≤L 0。
在上述过程中，滑片30的最大行程为s，且s＝L max-L min。滑片弹簧40的最大变形量为L 0-L min＝ΔL＞s。
可选地，若滑片30所受的最大压力差为F，单个滑片30采用的滑片弹簧40个数为n。则在本实施例中，n＝2，则单个滑片弹簧40所承受的最大压力为
Figure PCTCN2017118331-appb-000001
滑片弹簧40的刚度
Figure PCTCN2017118331-appb-000002
可选地，两个滑片孔31沿滑片30的中性层对称设置，即两个滑片孔31与中性层之间的距离X5及距离X6相等。
可选地，固定支架60上设置有多个导向结构50，且多个导向结构50沿固定支架60的竖直延伸方向上间隔设置。如图1所示，在本实施例中，固定支架60上设置有两个导向结构50，且两个导向结构50沿固定支架60的竖直延伸方向上间隔设置，且两个导向结构50与两个滑片孔31一一对应地设置。上述结构能够保证固定支架60的结构稳定性，延长固定支架60的使用寿命。
如图1和图2所示，在本实施例中，泵体组件还包括上法兰71及下法兰72。其中，转轴10穿设在上法兰71及下法兰72内，且气缸20设置在上法兰71与下法兰72之间。在泵体组件刚启动时，滑片30的头部和尾部之间还未形成压差，在滑片弹簧40的弹性力作用下，滑片30的头部贴紧气缸20。在泵体组件运行过程中，随着转轴10的旋转，滑片30在离心力、背压及弹性力的共同作用下从滑片槽111中伸出，并在滑片槽111中开始做往复直线运动，滑片30的头部与气缸20的内壁面接触。3个滑片30与气缸20的内壁面及上法兰71和下法兰72把气缸20的整个月牙腔分为3个独立腔室，3个腔室周期性的扩大、缩小，从而实现泵体组件的吸气、压缩和排气。
本申请还提供了一种流体机械(未示出)，包括上述的泵体组件。可选地，流体机械为压缩机。
本申请还提供了一种换热设备(未示出)，包括上述的流体机械。可选地，换热设备为空调。
实施例二
实施例二的泵体组件与实施例一的区别在于：固定支架60的结构不同。
如图11所示，固定支架60为工字型结构。这样，上述设置能够减小固定支架60的重量，使得泵体组件更加轻量化，提高泵体组件的工作效率、工作性能。
可选地，固定支架60上设置有减重孔，且减重孔避让导向结构50设置。
实施例三
实施例三的泵体组件与实施例一的区别在于：导向结构50的结构不同。
如图12所示，导向结构50包括凸台结构51。其中，凸台结构51设置在导向结构50的靠近固定支架60的一端，且凸台结构51能够与滑片弹簧40止挡配合。这样，凸台结构51能够对滑片弹簧40进行限位止挡，能够增加滑片弹簧40的弹性变形量，则工作人员可以根据需要对滑片弹簧40的长度进行合理选择。凸台结构51的结构简单，容易加工。
实施例四
实施例四的泵体组件与实施例一的区别在于：固定支架60的结构不同。
如图13至图15所示，固定支架60包括两个子支架62，且两个子支架62彼此远离的一端均具有卡接凸起61，各子支架62上均设置有一个导向结构50。这样，上述设置能够进一步减轻固定支架60的重量，实现固定支架60的轻量化设计。
如图14和图15所示，滑片槽111的槽宽W，两个限位结构111a之间的距离W1，其中，W≤W1。这样，在泵体组件启动或者运行过程中，上述设置能够保证固定支架60不会从限位结构111a内脱出，进而保证导向结构50的工作可靠性，提升泵体组件的结构稳定性。
如图13所示，固定支架60的端部具有卡接凸起61，转子部11的沿转轴10的轴向方向的端面上设置有限位凹部12，卡接凸起61嵌入限位凹部12内，且限位凹部12的深度H1与卡接凸起61的高度H2相等。这样，上述设置能够保证固定支架60与转子部11的连接更加稳固，且不会发生固定支架60与泵体组件的其他结构发生结构干涉，提高泵体组件的结构紧凑性。
从以上的描述中，可以看出，本发明上述的实施例实现了如下技术效果：
在泵体组件启动或者运行过程中，滑片弹簧套设在导向结构上以对滑片弹簧进行导向，则滑片弹簧不会发生折弯变形，能够保证滑片的头部始终与内腔的腔壁相接触，使得滑片紧贴气缸设置。这样，本申请中的泵体组件的滑片与内腔的腔壁始终紧贴设置，能够避免滑片的尾部撞击滑片槽或者滑片的头部撞击气缸的现象发生，进而延长滑片、气缸及转轴的使用寿命，减小泵体组件运行过程中产生的振动和噪声。此外，本申请中的泵体组件能够保证气缸的各个腔室的密封性，提升泵体组件的工作性能。
显然，上述所描述的实施例仅仅是本发明一部分的实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都应当属于本发明保护的范围。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、工作、器件、组件和/或它们的组合。
需要说明的是，本申请的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本申请的实施方式能够以除了在这里图示或描述的那些以外的顺序实施。
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (19)

  1. 一种泵体组件，其特征在于，包括：
    转轴(10)，具有转子部(11)，且所述转子部(11)上设置有多个滑片槽(111)；
    气缸(20)，所述转轴(10)穿设在所述气缸(20)内，且所述气缸(20)具有内腔(21)；
    多个滑片(30)，多个所述滑片(30)可滑动地设置在各所述滑片槽(111)内，所述滑片(30)的头部与所述内腔(21)的腔壁相接触；
    多个滑片弹簧(40)，设置在各所述滑片槽(111)内，且各所述滑片弹簧(40)位于各所述滑片(30)的尾部；
    多个导向结构(50)，设置在各所述滑片槽(111)内，且所述导向结构(50)沿所述滑片(30)的运动方向伸出，所述滑片弹簧(40)套设在所述导向结构(50)上。
  2. 根据权利要求1所述的泵体组件，其特征在于，所述滑片(30)的靠近所述滑片弹簧(40)的端面上设置有滑片孔(31)，且所述导向结构(50)伸入至所述滑片孔(31)内。
  3. 根据权利要求1所述的泵体组件，其特征在于，所述泵体组件还包括固定支架(60)，所述导向结构(50)通过所述固定支架(60)固定在所述滑片槽(111)内。
  4. 根据权利要求3所述的泵体组件，其特征在于，所述滑片槽(111)的槽壁上设置有限位结构(111a)，所述固定支架(60)卡设在所述限位结构(111a)内，以防止所述固定支架(60)相对于所述滑片槽(111)发生运动。
  5. 根据权利要求3或4所述的泵体组件，其特征在于，所述固定支架(60)呈板状，且所述导向结构(50)垂直于呈板状的所述固定支架(60)。
  6. 根据权利要求3或4所述的泵体组件，其特征在于，所述固定支架(60)为工字型结构。
  7. 根据权利要求6所述的泵体组件，其特征在于，所述固定支架(60)的端部具有卡接凸起(61)，所述转子部(11)的沿所述转轴(10)的轴向方向的端面上设置有限位凹部(12)，所述卡接凸起(61)嵌入所述限位凹部(12)内，且所述限位凹部(12)的深度H1与所述卡接凸起(61)的高度H2相等。
  8. 根据权利要求7所述的泵体组件，其特征在于，所述固定支架(60)包括两个子支架(62)，且两个所述子支架(62)彼此远离的一端均具有所述卡接凸起(61)，各所述子支架(62)上均设置有一个所述导向结构(50)。
  9. 根据权利要求3或4所述的泵体组件，其特征在于，所述导向结构(50)包括：
    凸台结构(51)，设置在所述导向结构(50)的靠近所述固定支架(60)的一端，且所述凸台结构(51)能够与所述滑片弹簧(40)止挡配合。
  10. 根据权利要求4所述的泵体组件，其特征在于，所述限位结构(111a)为开设在所述滑片槽(111)的槽壁上的限位槽。
  11. 根据权利要求4或10所述的泵体组件，其特征在于，同一个所述滑片槽(111)内，所述滑片槽(111)的相对设置的两个槽壁上均设置有所述限位结构(111a)，且两个所述限位结构(111a)的连线L1与所述滑片(30)的运动方向垂直设置。
  12. 根据权利要求11所述的泵体组件，其特征在于，所述滑片槽(111)的槽宽W，两个所述限位结构(111a)之间的距离W1，其中，W≤W1。
  13. 根据权利要求2所述的泵体组件，其特征在于，所述滑片(30)上设置有两个或者多个所述滑片孔(31)。
  14. 根据权利要求1至4中任一项所述的泵体组件，其特征在于，所述导向结构(50)为柱状结构，所述滑片弹簧(40)的内径D1与所述导向结构(50)的径向尺寸D3之差为ΔD1，其中，0.01mm≤ΔD1≤0.03mm。
  15. 根据权利要求2所述的泵体组件，其特征在于，所述滑片孔(31)包括顺次连接的第一孔段(311)和第二孔段(312)，所述导向结构(50)伸入至所述第一孔段(311)内，且所述第一孔段(311)的孔径D4与所述导向结构(50)的径向尺寸D3之差为ΔD2，其中，0.01mm≤ΔD2≤0.03mm；
    所述第二孔段(312)的孔径D5小于所述第一孔段(311)的孔径D4，且所述第二孔段(312)的孔径D5与所述滑片弹簧(40)的外径D2之差为ΔD3，其中，0.01mm≤ΔD3≤0.03mm。
  16. 根据权利要求15所述的泵体组件，其特征在于，当所述滑片(30)的头部完全位于所述滑片槽(111)内时，所述滑片弹簧(40)的长度为L min，所述滑片(30)的尾部与所述导向结构(50)之间的距离为X1，当所述滑片(30)伸入所述内腔(21)的长度最大时，所述滑片弹簧(40)的长度为L max，所述第一孔段(311)的深度为X2，所述第二孔段(312)的深度为X3，所述导向结构(50)的长度为X4，且所述滑片弹簧(40)的线径D0，其中，D0＝(D2-D1)/2，则满足关系：L max-4D0≤X4≤X1+X2+X3。
  17. 根据权利要求3或4所述的泵体组件，其特征在于，所述固定支架(60)上设置有多个所述导向结构(50)，且多个所述导向结构(50)沿所述固定支架(60)的竖直延伸方向上间隔设置。
  18. 一种流体机械，其特征在于，包括权利要求1至17中任一项所述的泵体组件。
  19. 一种换热设备，其特征在于，包括权利要求18所述的流体机械。
PCT/CN2017/118331 2017-09-29 2017-12-25 泵体组件、流体机械及换热设备 Ceased WO2019061898A1 (zh)

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