WO2021098314A1 - 泵体组件、换热设备、流体机械及其运转方法 - Google Patents

泵体组件、换热设备、流体机械及其运转方法 Download PDF

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Publication number
WO2021098314A1
WO2021098314A1 PCT/CN2020/110701 CN2020110701W WO2021098314A1 WO 2021098314 A1 WO2021098314 A1 WO 2021098314A1 CN 2020110701 W CN2020110701 W CN 2020110701W WO 2021098314 A1 WO2021098314 A1 WO 2021098314A1
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WO
WIPO (PCT)
Prior art keywords
pressure relief
piston
pump body
body assembly
cylinder
Prior art date
Application number
PCT/CN2020/110701
Other languages
English (en)
French (fr)
Inventor
董明珠
胡余生
魏会军
徐嘉
杜忠诚
任丽萍
杨森
李直
张培林
梁社兵
史正良
张荣婷
丁宁
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 EP20890323.7A priority Critical patent/EP4006345A4/en
Priority to JP2022511003A priority patent/JP7353466B2/ja
Priority to US17/639,888 priority patent/US11971031B2/en
Publication of WO2021098314A1 publication Critical patent/WO2021098314A1/zh

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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
    • 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
    • F04C18/22—Rotary-piston pumps specially adapted for elastic fluids of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
    • 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
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the present disclosure is based on the application with the CN application number 201911158497.9 and the filing date on November 22, 2019, and claims its priority.
  • the disclosure of the CN application is hereby incorporated into the present disclosure as a whole.
  • the present disclosure relates to the field of heat exchange systems, and in particular, to a pump body assembly, heat exchange equipment, fluid machinery and operating methods thereof.
  • the rotary shaft drives the piston to rotate
  • the piston drives the piston sleeve to rotate in the cylinder.
  • the piston reciprocates relative to the rotating shaft and the piston sleeve respectively, and the two reciprocating movements are perpendicular to each other. In this process, suction, compression and exhaust are realized.
  • the radial distance between the piston and the inner diameter of the cylinder changes periodically.
  • the radial distance between the piston and the inner diameter of the cylinder keeps increasing; in the process of compression and exhaust, the distance keeps decreasing until it reaches the order of 10 -2 mm.
  • a pump body assembly including: a piston; a rotating shaft; a piston sleeve, the rotating shaft drives the piston to reciprocate in the piston sleeve while rotating; the cylinder, the piston sleeve is located in the cylinder, and the outer circumference of the piston
  • a compression cavity is formed between the wall and the inner wall of the cylinder, and a pressure relief recess is provided on the outer peripheral wall of the piston or the inner wall of the cylinder corresponding to the compression cavity.
  • other parts of the outer peripheral wall of the piston except where the pressure relief recess is located can be adapted to the inner wall of the cylinder.
  • the pressure relief recess extends along the circumference of the piston.
  • the sum of the arc lengths between the two ends of the pressure relief recess in the rotation direction of the piston and the corresponding two ends of the compression chamber is greater than or equal to 2 mm.
  • the cylinder further has an exhaust passage, and the arc length between an end close to the exhaust passage of the pressure relief recess in the rotation direction of the piston and the exhaust passage is greater than or equal to 1 mm.
  • the distance between the pressure relief recess and the edge of the piston is greater than or equal to 1 mm; or in the axial direction of the shaft, the distance between the pressure relief recess and the edge of the cylinder is greater than or equal to 1 mm.
  • the pressure relief recess includes at least one pressure relief groove.
  • the multiple pressure relief grooves communicate with each other or are independent of each other.
  • the groove width of each pressure relief groove is greater than or equal to 0.5 mm.
  • the groove depth of each pressure relief groove is greater than or equal to 0.1 mm.
  • the cross-sectional area of all pressure relief grooves is greater than or equal to 0.025 square millimeters.
  • the ratio of the sum of the cross-sectional areas of all pressure relief grooves to the cross-sectional area of the piston along the axis perpendicular to the cylinder is greater than or equal to 0.001 and less than or equal to 0.5.
  • the cross-section of each pressure relief groove is rectangular or fan-shaped.
  • the pressure relief groove is one and extends along the circumference of the piston or the circumferential direction of the cylinder; or there are two pressure relief grooves and is cross-shaped; or the pressure relief groove is three and is H-shaped; or There are three grooves in the shape of an "I"; or there are multiple pressure relief grooves in the shape of a fishbone; or there are two pressure relief grooves, and the first pressure relief groove extends along the circumference of the piston or the circumference of the cylinder, The second pressure relief groove is annular and crosses the first pressure relief groove.
  • the ratio of the cavity volume of the pressure relief recess to the displacement of the pump body assembly is greater than or equal to 0.001 and less than or equal to 0.02.
  • a fluid machine including the above-mentioned pump body assembly.
  • the fluid machine is a compressor.
  • a heat exchange device including the above-mentioned fluid machine.
  • a method for operating a fluid machine is provided.
  • the fluid machine is the above-mentioned fluid machine.
  • the cylinder of the fluid machine has an intake passage, a pressure relief passage, and an exhaust passage arranged at intervals, and the pressure relief passage is connected to the The cavity of the cylinder is connected through the pressure relief port, and the exhaust channel is connected with the cavity of the cylinder through the exhaust port.
  • the operation method includes: when the fluid machine is exhausted, the pressure relief recess of the pump body assembly of the fluid machine is directly or indirectly The ground is in communication with the pressure relief port and is separated from the exhaust port at the same time.
  • FIG. 1 shows a schematic diagram of the internal structure of the pump body assembly of the first embodiment of the pump body assembly of the present disclosure
  • Figure 2 shows a schematic diagram of the internal structure of the cylinder in Figure 1;
  • Fig. 3 shows a three-dimensional schematic diagram of the piston in Fig. 1;
  • Figure 4 shows a front view of the piston in Figure 3;
  • Figure 5 shows a cross-sectional view of the A-A side of the piston in Figure 4.
  • Fig. 6 shows a cross-sectional view of the B-B plane in Fig. 4, wherein the cross-sectional shape of the pressure relief recess is semicircular;
  • FIG. 7 shows an enlarged view at D in FIG. 6
  • Figure 8 shows a cross-sectional view of the C-C plane in Figure 5;
  • Fig. 9 shows a comparison diagram of the change trend of the exhaust velocity of the pump body assembly with the angle of rotation in the first embodiment
  • FIG. 10 shows a cross-sectional view of the piston of the third embodiment of the pump body assembly of the present disclosure (the viewing angle is similar to that of FIG. 6), in which the cross-sectional shape of the pressure relief recess is rectangular;
  • Figure 11 shows an enlarged view at E in Figure 10
  • FIG. 12 shows a schematic structural diagram of a piston of a fourth embodiment of the pump body assembly of the present disclosure
  • FIG. 13 shows a schematic structural diagram of a piston of Embodiment 5 of the pump body assembly of the present disclosure
  • Fig. 14 shows a schematic structural view of a piston of the sixth embodiment of the pump body assembly of the present disclosure
  • FIG. 15 shows a schematic structural diagram of a piston of the seventh embodiment of the pump body assembly of the present disclosure
  • Figure 16 shows a schematic structural view of the piston of the eighth embodiment of the pump body assembly of the present disclosure
  • FIG. 17 shows a schematic structural diagram of a piston of a ninth embodiment of the pump body assembly of the present disclosure
  • Fig. 18 shows a schematic structural view of the piston of the tenth embodiment of the pump body assembly of the present disclosure.
  • orientation words used such as “up, down, top, bottom” are usually directed to the direction shown in the drawings, or refer to the vertical, In terms of vertical or gravitational direction; similarly, for ease of understanding and description, “inner and outer” refers to the inner and outer relative to the contour of each component itself, but the above-mentioned directional words are not used to limit the present disclosure.
  • the exhaust channel area is the product of the distance between the extruded end face and the radial direction of the cylinder and the section height.
  • the high-pressure gas outside the exhaust port must first flow through the space between the piston extrusion end surface and the cylinder before reaching the exhaust port.
  • the exhaust area is much smaller than the exhaust port area.
  • the effective exhaust area also decreases, resulting in a large exhaust resistance and an increase in exhaust pressure, which is higher than the designed exhaust pressure ,
  • the entire compression chamber has over-compression, which affects the energy efficiency of the compressor.
  • the overcompression problem is alleviated to a certain extent by opening a pressure relief channel on the cylinder.
  • the pressure relief channel can only improve the overcompression problem near the pressure relief channel, and there is still overcompression at locations far away from the pressure relief channel and the exhaust channel.
  • the embodiments of the present disclosure provide a pump body assembly, a heat exchange device, a fluid machine and an operation method thereof, which can improve the overcompression phenomenon of the pump body assembly during exhaust.
  • the fluid machine includes the following pump body components.
  • the heat exchange equipment includes the following fluid machinery.
  • the fluid machine is a compressor.
  • the pump body assembly includes a piston 1, a rotating shaft 2, a piston sleeve 3, and a cylinder 4.
  • the rotating shaft 2 drives the piston 1 to reciprocate in the piston sleeve 3 while rotating.
  • the piston sleeve 3 is located in the cylinder 4, and a compression chamber 5 is formed between the outer peripheral wall of the piston 1 and the inner wall of the cylinder 4.
  • a pressure relief recess 11 is provided at a position corresponding to the compression chamber 5 on the outer peripheral wall of the piston 1 or the inner wall of the cylinder.
  • the pressure relief recess 11 is opened on the outer peripheral wall of the piston 1.
  • the piston sleeve 3 is located in the cylinder, and a compression chamber 5 is formed between the outer peripheral wall of the piston 1 and the inner wall of the cylinder 4, and the outer peripheral wall of the piston 1 or the inner wall of the cylinder 4 corresponds to the position of the compression chamber 5
  • a pressure relief recess 11 is provided.
  • the outer peripheral wall of the piston 1 except for the position where the pressure relief recess 11 is located can be adapted to the inner wall of the cylinder 4 during the movement.
  • the pressure relief recess 11 is to further alleviate the overcompression of the gas in the compression chamber 5, and the gas in the compression chamber 5 still needs to have a certain compression ratio. Therefore, the outer peripheral wall of the piston 1 except for the pressure relief recess 11 is located at the same position as The inner wall of the cylinder 4 is adapted.
  • the pressure relief recess 11 extends in the circumferential direction of the piston 1. It should be noted that the aforementioned pressure relief recess 11 extends along the circumferential direction of the piston 1 does not mean that the pressure relief recess 11 can only be a strip-shaped groove, but that its general extension trend is along the circumferential direction of the piston 1. of. In other words, the pressure relief recesses 11 are distributed along the circumference of the piston 1. The function of the pressure relief recesses 11 is to alleviate the overcompression of the gas in the compression chamber 5. The pressure relief recesses 11 are distributed along the circumference of the piston 1, so that the pressure relief recesses 11 are distributed along the circumference of the piston 1. The depressed portion 11 can cover more of the compression chamber 5, and the gas in the compression chamber 5 that is not at the position of the exhaust port can flow to the exhaust port through the pressure relief recess 11, so as to better alleviate over-compression.
  • the cylinder 4 also has an exhaust passage 41, and the arc length between the end close to the exhaust passage 41 and the exhaust passage 41 of the two ends of the pressure relief recess 11 along the rotation direction of the piston 1 is greater than Equal to 1 millimeter.
  • this distance corresponds to the figure L1, that is, L1 is greater than or equal to 1 mm.
  • the gas at the exhaust port has a high air pressure, so the distance of L1 needs to be limited. If the sealing distance is too small, high-pressure gas may enter the suction channel 43 through the pressure relief recess 11, affecting the suction of the pump body components. gas.
  • the air pressure of the gas at the suction port is relatively low, so only a certain sealing distance needs to be set for the sealing distance L2.
  • the pressure relief recess 11 includes at least one pressure relief groove.
  • the multiple pressure relief grooves communicate with each other or are independent of each other.
  • the pressure relief recess 11 is to alleviate the over-compression of the pump body components. According to the compression amount and power of the pump body components, the over-compression condition of each pump body component is different. Different forms of pressure relief recesses 11 are used for conditions.
  • a pressure relief groove is used and extends along the circumference of the piston 1.
  • the groove width of each pressure relief groove is greater than or equal to 0.5 mm.
  • the groove depth of each pressure relief groove is greater than or equal to 0.1 mm.
  • the cross-sectional area of all pressure relief grooves is greater than or equal to 0.025 square millimeters.
  • the width, depth and cross-section of the pressure relief groove The area needs to be limited. In some embodiments, the groove width is 0.8 mm, the groove depth is 0.2 mm, and the cross-sectional area of the groove is 0.16 square mm.
  • the ratio of the sum of the cross-sectional area of all pressure relief grooves to the cross-sectional area of the piston 1 along the axis perpendicular to the cylinder 4 is greater than or equal to 0.001 and less than or equal to 0.5.
  • the size of the cross-sectional area of the piston 1 is determined according to the compression amount of the pump body assembly.
  • the pressure relief groove is to increase the effective exhaust area at the exhaust end of the pump body assembly, thus limiting the gap between the two
  • the ratio of is not only to ensure that the pressure relief groove plays a role in alleviating the over-compression, but also does not affect the compression of the pump body components as much as possible.
  • each pressure relief groove is rectangular or fan-shaped.
  • the cross-section of the pressure relief groove is rectangular or fan-shaped and can be directly processed by a milling machine.
  • the cross-sectional area of the pressure relief groove is semicircular.
  • the distance between the pressure relief recess 11 and the edge of the piston 1 is greater than or equal to 1 mm.
  • the piston 1 moves in the cylinder, the upper and lower end surfaces of the cylinder deform into the piston cavity of the cylinder 4 under the action of gas force.
  • the pressure relief recess 11 and the edge of the piston 1 The distance between them is greater than or equal to 1 mm.
  • the rotating shaft 2 in the pump body assembly drives the piston 1 to rotate, the piston 1 only has relative reciprocating motion relative to the piston sleeve 3, and the two reciprocating motions are perpendicular to each other.
  • suction, compression and exhaust are realized.
  • the pump body assembly has a single cylinder and double compression chamber structure, and the two compression chambers 5 are independent of each other.
  • the suction start angle is 0°
  • the suction is completed at 0° ⁇ 180°
  • the compression and exhaust are completed at 80° ⁇ 360°.
  • the other compression chamber 5 is offset by 180°, which means that when one compression chamber 5 completes suction and is about to enter the compression phase, the other compression chamber 5 completes exhaust and is about to enter the suction phase.
  • the exhaust area of the compression chamber 5 is the sum of the area of the exhaust port and the pressure relief port:
  • ⁇ is the radial clearance between the head of the piston 1 and the inner circle of the cylinder 4.
  • ⁇ is the percentage of effective contacts.
  • V' is the volume change rate of the compression chamber 5 of the rotary cylinder.
  • V’ (V ⁇ sin ⁇ )/4
  • V is the compressor displacement
  • ⁇ is the angular velocity of the rotating shaft.
  • the ratio of the cavity volume of the pressure relief recess 11 to the displacement of the pump body assembly is greater than or equal to 0.001 and less than or equal to 0.02.
  • the piston head is provided with a pressure relief recess, which will increase the actual suction volume of the pump body during the suction process.
  • the high-pressure gas in the pressure relief recess 11 will enter the next suction cycle. Therefore, if the pressure relief recess 11 is too large, the suction process will be affected. Therefore, the ratio of the cavity volume of the pressure relief recess 11 on the entire piston to the displacement of the pump body assembly is greater than or equal to 0.001 and less than or equal to 0.02.
  • the fluid machine is the above-mentioned fluid machine.
  • the cylinder of the fluid machine has an intake passage, a pressure relief passage 42 and an exhaust passage 41 arranged at intervals, and the pressure relief passage 42 and the cavity of the cylinder pass through
  • the pressure port is connected, and the exhaust passage 41 communicates with the cavity of the cylinder through the exhaust port.
  • the operation method includes: when the fluid machine is exhausted, the pressure relief recess 11 of the pump body assembly of the fluid machine is directly or indirectly connected to the pressure relief The port is connected and separated from the exhaust port at the same time.
  • the compression chamber 5 leaves the position of the exhaust port, and the gas in the compression chamber 5 can only be released through the pressure relief port.
  • the fluid mechanical pump The pressure relief recess 11 of the body assembly directly or indirectly communicates with the pressure relief port, and at the same time is separated from the exhaust port.
  • the main difference between this embodiment and the first embodiment is that the pressure relief recess 11 is provided on the cylinder 4.
  • the pump body assembly includes a piston 1, a rotating shaft 2, a piston sleeve 3, and a cylinder 4.
  • the rotating shaft 2 drives the piston 1 to reciprocate in the piston sleeve 3 while rotating.
  • the piston sleeve 3 is located in the cylinder 4, and a compression chamber 5 is formed between the outer peripheral wall of the piston 1 and the inner wall of the cylinder 4, and a pressure relief recess 11 is provided on the inner wall of the cylinder 4 at a position corresponding to the compression chamber 5.
  • the piston sleeve 3 is located in the cylinder, and a compression chamber 5 is formed between the outer peripheral wall of the piston 1 and the inner wall of the cylinder.
  • the outer peripheral wall of the piston 1 or the inner wall of the cylinder 4 is provided at a position corresponding to the compression chamber 5
  • the distance between the pressure relief recess 11 and the edge of the cylinder 4 is greater than or equal to 1 mm.
  • the cross section of the pressure relief groove is rectangular, which is more convenient to process than a semicircle. Only one cutter head needs to be moved during the process. direction.
  • the fourth to sixth embodiments are embodiments with one pressure relief groove.
  • the seventh to tenth embodiments are embodiments in which there are multiple pressure relief grooves.
  • the pressure relief groove is to relieve the over-compression of the pump body components. According to the compression amount and power of the pump body components, the over-compression condition of each pump body component is different. In actual use, it can be based on different conditions Different forms of pressure relief grooves are used. Considering the convenience of processing, in the first embodiment, the pressure relief groove is opened along the circumference of the piston 1, and there is only one.
  • the pressure relief groove is one and extends along the axis of the rotating shaft.
  • the pressure relief groove is one and has an included angle with the axial direction of the rotating shaft, and the included angle is not equal to 90 degrees.
  • the first embodiment there is one pressure relief groove.
  • the difference from the first embodiment is that the shape of the pressure relief groove is different from that of the first embodiment.
  • the pressure relief groove is one and annular.
  • the difference from the first embodiment is that the number of pressure relief grooves is different from that of the first embodiment.
  • the pressure relief grooves are two and are cross-shaped.
  • the pressure relief grooves are three and are H-shaped.
  • the pressure relief grooves are multiple and have a fishbone shape.
  • the first pressure relief groove extends along the circumference of the piston 1 or the circumferential direction of the cylinder 4, and the second pressure relief groove is ring-shaped and connected with The first pressure relief groove crosses.
  • the piston sleeve is located in the cylinder, and a compression cavity is formed between the outer peripheral wall of the piston and the inner wall of the cylinder, and a pressure relief recess is provided on the outer peripheral wall of the piston or the inner wall of the cylinder corresponding to the compression cavity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Reciprocating Pumps (AREA)

Abstract

一种泵体组件、换热设备、流体机械及其运转方法，其中泵体组件包括：活塞（1）；转轴（2）；活塞套（3），转轴（2）驱动活塞（1）在转动的同时在活塞套（3）内往复运动；气缸（4），活塞套（3）位于气缸（4）内，且活塞（1）的外周壁与气缸（4）的内壁之间形成压缩腔（5），活塞（1）的外周壁或气缸（4）的内壁上对应于压缩腔（5）的位置设置有泄压凹部（11）。

Description

泵体组件、换热设备、流体机械及其运转方法
相关申请的交叉引用
本公开是以CN申请号为201911158497.9，申请日为2019年11月22日的申请为基础，并主张其优先权，该CN申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及换热系统领域，具体而言，涉及一种泵体组件、换热设备、流体机械及其运转方法。
背景技术
在发明人知晓的一种转缸活塞压缩机的泵体结构及转缸活塞压缩机中，转轴驱动活塞旋转，活塞带动活塞套在汽缸内旋转。而活塞分别相对于转轴和活塞套往复运动，且两个往复运动相互垂直。在此过程中实现吸气、压缩和排气。
在吸气、压缩、排气过程中，活塞与气缸内径的径向距离周期性变化。在吸气过程中，活塞与气缸内径的径向距离不断增大；在压缩、排气过程中，距离不断减小，直至10 -2mm量级。
发明内容
根据本公开的一个方面，提供了一种泵体组件，包括：活塞；转轴；活塞套，转轴驱动活塞在转动的同时在活塞套内往复运动；气缸，活塞套位于气缸内，且活塞的外周壁与气缸的内壁之间形成压缩腔，活塞的外周壁或气缸的内壁上对应于所述压缩腔的位置设置有泄压凹部。
在一些实施例中，在运动的过程中，活塞的外周壁除泄压凹部所在的位置的其他部分能够与气缸的内壁适配。
在一些实施例中，泄压凹部沿活塞的周向延伸。
在一些实施例中，泄压凹部沿活塞的旋转方向的两端距离压缩腔相应两端的弧长之和大于等于2毫米。
在一些实施例中，气缸还具有排气通道，泄压凹部沿活塞的旋转方向的两端中靠近排气通道的一端与排气通道之间的弧长大于等于1毫米。
在一些实施例中，在转轴的轴线方向上，泄压凹部与活塞的边缘之间的距离大于等于1毫米；或在转轴的轴线方向上，泄压凹部与气缸的边缘之间的距离大于等于1毫米。
在一些实施例中，泄压凹部包括至少一条泄压槽，当泄压槽为多个时，多个泄压槽彼此连通或彼此独立。
在一些实施例中，各泄压槽的槽宽大于等于0.5毫米。
在一些实施例中，各泄压槽的槽深大于等于0.1毫米。
在一些实施例中，所有泄压槽的横截面积大于等于0.025平方毫米。
在一些实施例中，所有泄压槽的横截面积之和与活塞沿垂直于气缸轴线的横截面积的比值大于等于0.001且小于等于0.5。
在一些实施例中，各泄压槽的横截面为矩形或者扇形。
在一些实施例中，泄压槽为一条且沿活塞的周向或者气缸的周向延伸；或者泄压槽为两条且呈十字形；或者泄压槽为三条且呈H形；或者泄压槽为三条且呈“工”字形；或者泄压槽为多条且呈鱼骨形；或者泄压槽为两条，且第一条泄压槽沿活塞的周向或者气缸的周向延伸，第二条泄压槽呈环状并与第一条泄压槽交叉。
在一些实施例中，泄压凹部的凹腔体积与泵体组件的排量之比大于等于0.001且小于等于0.02。
根据本公开的另一个方面，提供了一种流体机械，包括上述泵体组件。
在一些实施例中，流体机械是压缩机。
根据本公开的另一个方面，提供了一种换热设备，包括上述流体机械。
根据本公开的另一个方面，提供了一种流体机械的运转方法，流体机械是上述流体机械，流体机械的气缸具有间隔设置的吸气通道、泄压通道和排气通道，且泄压通道与气缸的腔体通过泄压口连通，排气通道与气缸的腔体通过排气口连通，运转方法包括：在流体机械处于排气结束时，流体机械的泵体组件的泄压凹部直接或间接地与泄压口连通，同时与排气口脱离。
附图说明
构成本公开的一部分的说明书附图用来提供对本公开的进一步理解，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：
图1示出了本公开泵体组件的实施例一的泵体组件的内部结构示意图；以及
图2示出了图1中气缸的内部结构示意图；
图3示出了图1中活塞的立体示意图；
图4示出了图3中活塞的主视图；
图5示出了图4中活塞的A-A面的剖视图；
图6示出了图4中B-B面的剖视图，其中泄压凹部的横截面的形状为半圆形；
图7示出了图6中D处的放大图；
图8示出了图5中C-C面的剖视图；
图9示出了实施例一中的泵体组件的排气速度随转角变化趋势的对比图；
图10示出了本公开泵体组件的实施例三的活塞的截面视图(其视角相似于图6)，其中泄压凹部的横截面的形状为矩形；
图11示出了图10中E处的放大图；
图12示出了本公开泵体组件的实施例四的活塞的结构示意图；
图13示出了本公开泵体组件的实施例五的活塞的结构示意图；
图14示出了本公开泵体组件的实施例六的活塞的结构示意图；
图15示出了本公开泵体组件的实施例七的活塞的结构示意图；
图16示出了本公开泵体组件的实施例八的活塞的结构示意图；
图17示出了本公开泵体组件的实施例九的活塞的结构示意图；
图18示出了本公开泵体组件的实施例十的活塞的结构示意图。
其中，上述附图包括以下附图标记：
1、活塞；11、泄压凹部；2、转轴；3、活塞套；4、气缸；41、排气通道；42、泄压通道；43、吸气通道；5、压缩腔。
具体实施方式
需要说明的是，在不冲突的情况下，本公开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公开。
需要指出的是，除非另有指明，本公开使用的所有技术和科学术语具有与本公开所属技术领域的普通技术人员通常理解的相同含义。
在本公开中，在未作相反说明的情况下，使用的方位词如“上、下、顶、底”通常是针对附图所示的方向而言的，或者是针对部件本身在竖直、垂直或重力方向上而言的；同样地，为便于理解和描述，“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公开。
经研究发现，排气的通道面积为挤压端面与气缸径向之间距离与截面高度的乘积。排气过程中，排气口以外的高压气体要先流经活塞挤压端面与气缸之间的空间后，才能到达排气口，但是随着活塞挤压端面与气缸径向之间距离不断减小，此时排气面积远小于排气口面积，随着距离的不断减小，有效排气面积也不断减小，从而导致排气阻力大，排气压力升高，高于设计排气压力，整个压缩腔出现过压缩现象，影响压缩机能效。
在发明人知晓的另一种方案中，通过在气缸上开设泄压通道，一定程度上缓解了过压缩问题。但经研究发现，由于整个活塞挤压端面的气体都是高压气体，泄压通道仅能改善泄压通道附近位置的过压缩问题，远离泄压通道及排气通道位置依然存在过压缩现象。
有鉴于此，本公开实施例提了一种泵体组件、换热设备、流体机械及其运转方法，能够改善泵体组件在排气时的过压缩现象。具体的，流体机械包括下述泵体组件。换热设备包括下述的流体机械。在一些实施例中，流体机械为压缩机。
实施例一
如图1至图9所示，泵体组件包括活塞1、转轴2、活塞套3和气缸4。转轴2驱动活塞1在转动的同时在活塞套3内往复运动。活塞套3位于气缸4内，且活塞1的外周壁与气缸4的内壁之间形成压缩腔5。活塞1的外周壁或气缸的内壁上对应于压缩腔5的位置设置有泄压凹部11。
需要说明的是，在本实施例中，泄压凹部11开设于活塞1的外周壁上。
应用本公开的技术方案，活塞套3位于气缸内，且活塞1的外周壁与气缸4的内壁之间形成压缩腔5，活塞1的外周壁或气缸4的内壁上对应于压缩腔5的位置设置有泄压凹部11。当泵体组件处于排气过程中时，远离排气口的气体能够通过泄压凹部11向排气口处流动，增大了排气面积，进一步地改善了泵体组件在排气时出现过压缩的情况。
如图1所示，活塞1的外周壁除泄压凹部11所在的位置的其他部分在运动的过程中能够与气缸4的内壁适配。泄压凹部11是为了进一步缓解压缩腔5内气体的过压缩情况，压缩腔5内的气体还是需要保证有一定的压缩比，因此活塞1的外周壁除泄压凹部11所在的位置，需要与气缸4的内壁适配。
如图3和图4所示，泄压凹部11沿活塞1的周向延伸。需要说明的是，上述泄 压凹部11沿活塞1的周向延伸并不是说泄压凹部11只能是一个条状的槽，而是说其大体上的延伸趋势是沿着活塞1的周向的。或者说，泄压凹部11沿着活塞1的周向进行分布，泄压凹部11的作用是为了缓解压缩腔5内气体的过压缩情况，泄压凹部11沿活塞1的周向分布，使得泄压凹部11能够覆盖压缩腔5更多的范围，压缩腔5内不在排气口位置的气体能够通过泄压凹部11流向排气口，从而起到更好的缓解过压缩的作用。
如图1、图3、图4、图5所示，泄压凹部11沿活塞1的旋转方向的两端分别距离压缩腔5相应两端的弧长之和大于等于2毫米。考虑到泵体组件两个容积腔的独立性及避免串气的需要，在排气结束时刻，泄压凹部11不能贯穿排气口和吸气通道43，因此在活塞1开设泄压凹部11时需要在两端留有一定的密封距离。如图1所示，当泵体组件排气结束时，活塞1的两端位置与压缩腔5对应的两端位置大致重合，本实施例中以活塞1的两端为基准，如图5所示，密封距离即为L1和L2，L1和L2的长度之和大于等于2毫米。
如图1和图5所示，气缸4还具有排气通道41，泄压凹部11沿活塞1的旋转方向的两端中靠近排气通道41的一端与排气通道41之间的弧长大于等于1毫米。本实施例中，此段距离对应图示L1，即L1大于等于1毫米。位于排气口位置的气体具有较高的气压，因此需要对L1的距离进行限制，如果密封距离过小，高压的气体可能会通过泄压凹部11进入吸气通道43内，影响泵体组件吸气。位于吸气口位置的气体的气压相对较低，因此对于密封距离L2只需要设置一定的密封距离即可。
在本公开的一些实施例中，泄压凹部11包括至少一条泄压槽，当泄压槽为多个时，多个泄压槽彼此连通或彼此独立。泄压凹部11是为了缓解泵体组件过压缩的现象，根据泵体组件的压缩量、功率等情况，每个泵体组件过压缩的状况是不同的，实际使用的过程中，可以根据不同的状况采用不同形式的泄压凹部11。
在图3至图5所示的具体实施例中，采用的是一条泄压槽，并且沿着活塞1的周向延伸。
如图6至图8所示，各泄压槽的槽宽大于等于0.5毫米。可选地，各泄压槽的槽深大于等于0.1毫米。可选地，所有泄压槽的横截面积大于等于0.025平方毫米。对于所有的泄压槽而言，最终都是用来排出压缩末端的高压气体，泄压槽本身也是一段排气的通道，同时需要考虑加工工艺问题，对泄压槽的宽度、深度以及横截面积需要有一定的限制，在一些实施例中，槽宽为0.8毫米，槽深为0.2毫米，槽的横截面积 为0.16平方毫米。
如图6至图8所示，所有泄压槽的横截面积之和与活塞1沿垂直于气缸4轴线的横截面积的比值大于等于0.001且小于等于0.5。如图10所示，活塞1横截面积的大小根据泵体组件的压缩量确定的，泄压槽的作用是为了增大泵体组件排气末端的有效排气面积，因此限制二者之间的比值大小既可以保证泄压槽起到缓解过压缩的作用，也尽可能的不对泵体组件的压缩量造成影响。
可选地，各泄压槽的横截面为矩形或者扇形。泄压槽的横截面为矩形或者扇形可以通过铣床直接加工出来。本实施例中，泄压槽的横截面积为半圆形。
在转轴2的轴线方向上，泄压凹部11与活塞1的边缘之间的距离大于等于1毫米。考虑到活塞1在气缸内运动，气缸上下端面在气体力作用下向气缸4的活塞腔内变形，为了避免气缸4变形后与活塞1边缘出现“剐蹭”，泄压凹部11与活塞1的边缘之间的距离大于等于1毫米。
如图9所示，泵体组件中转轴2驱动活塞1旋转、活塞1相对于活塞套3仅存在相对往复运动，且两个往复运动相互垂直，在此过程中实现吸气、压缩和排气。泵体组件中为单气缸双压缩腔结构，两个压缩腔5相互独立。对单个容积腔而言，吸气开始角度为0°，在0°～180°完成吸气，1在80°～360°完成压缩和排气。另外一个压缩腔5与之错位180°，此意味着当一个压缩腔5完成吸气即将进入压缩阶段的同时，另外一个压缩腔5完成排气即将进入吸气阶段。
在排气初始阶段，压缩腔5的排气面积为排气口和泄压口的面积之和：
S＝(πd1^2)/4+(πd2^2)/4，
其中，d1为排气口直径；d2为泄压口直径。
在排气末端，由于活塞1头部与气缸4内圆径向距离不断减小，此时，压缩腔5的排气面积与活塞1头部与气缸4径向距离以及排气口周长和泄压口周长之和成线性关系：
S＝(πd1+πd2)×Δ，
其中，Δ为活塞1头部与气缸4内圆的径向间隙。
在压缩腔5逐渐脱离排气口的过程中，压缩腔5与排气口重叠的区域逐渐减小，此时，有效排气面积S：
S＝δ×(πd1+πd2)×Δ
δ为有效接触占比。
定义转缸压缩机的理论排气速度v的计算公式如下：
v＝V’/S
V’为转缸压缩腔5的容积变化率。
定义开始压缩的角度为0°角，此时V’计算公式如下：
V’＝(V×ω×sinθ)/4
V为压缩机排量；ω为转轴转动的角速度。
在整个排气阶段，压缩腔5的有效排气面积、理论排气速度随转角的变化规律见图9所示，可以明确看到在压缩末端，压缩腔5的有效排气面积逐渐减小，理论排气速度不断增大；此时对应的排气阻力就不断增加，末端排气出现较大的过压缩现象，严重影响压缩机能效。具体如附图9所示，组合泄压槽的排气速度随转角变化的曲线也如附图9所示。
如图1所示，泄压凹部11的凹腔体积与泵体组件的排量之比大于等于0.001且小于等于0.02。活塞头部开设泄压凹部，在吸气过程中会增加泵体实际吸气量。在排气过程中，泄压凹部11内的高压气体会进去下一个吸气循环，因此，若泄压凹部11过大就会影响吸气过程。故整个活塞上的泄压凹部11的凹腔体积与泵体组件的排量之比大于等于0.001且小于等于0.02。
本公开的流体机械的运转方法，流体机械是上述流体机械，流体机械的气缸具有间隔设置的吸气通道、泄压通道42和排气通道41，且泄压通道42与气缸的腔体通过泄压口连通，排气通道41与气缸的腔体通过排气口连通，运转方法包括：在流体机械处于排气结束时，流体机械的泵体组件的泄压凹部11直接或间接地与泄压口连通，同时与排气口脱离。在排气结束时刻，压缩腔5离开排气口位置，压缩腔5内的气体只能够通过泄压口进行泄压，为了达到泄压效果同时避免串气，排气结束时刻，流体机械的泵体组件的泄压凹部11直接或间接地与泄压口连通，同时与排气口脱离。
实施例二
本实施例与实施例一主要的区别是，泄压凹部11开设于气缸4上。
具体的，泵体组件包括活塞1、转轴2、活塞套3、气缸4，转轴2驱动活塞1在转动的同时在活塞套3内往复运动。气缸，活塞套3位于气缸4内，且活塞1的外周壁与气缸4的内壁之间形成压缩腔5，气缸4的内壁上对应于压缩腔5的位置设置有泄压凹部11。
应用本公开的技术方案，活塞套3位于气缸内，且活塞1的外周壁与气缸的内壁 之间形成压缩腔5，活塞1的外周壁或气缸4的内壁上对应于压缩腔5的位置设置有泄压凹部11。当泵体组件处于排气过程中时，远离排气口的气体能够通过泄压凹部11从排气口排出，增大了排气面积，进一步地改善了泵体组件在排气时，出现过压缩的情况。
可选地，在转轴2的轴线方向上，泄压凹部11与气缸4的边缘之间的距离大于等于1毫米。
实施例三
本实施例与实施例一主要的区别是，如图10和图11所示，泄压槽的横截面为矩形，矩形相对半圆形加工起来更加方便，加工的过程中只需要移动刀头一个方向。
当然，根据泄压槽个数的不同，本公开还另提供了多种实施例。实施例四至实施例六是泄压槽为一条的实施例。实施例七至实施例十为泄压槽是多个的实施例。泄压槽是为了缓解泵体组件过压缩的现象，根据泵体组件的压缩量、功率等情况，每个泵体组件过压缩的状况是不同的，实际使用的过程中，可以根据不同的状况采用不同形式的泄压槽。考虑到加工的方便性，实施例一中泄压槽沿活塞1的周向开设，并且只有一条。
实施例四
与实施例一相同，泄压槽为一条。与实施例一的区别在于，泄压槽的延伸方向与实施例一是不同的。
在图12所示的具体实施例中，泄压槽为一条且沿转轴的轴线方向延伸。
实施例五
与实施例一相同，泄压槽为一条。与实施例一的区别在于，泄压槽的延伸方向与实施例一是不同的。
在图13所示的具体实施例中，泄压槽为一条且与转轴的轴线方向之间具有夹角，且所述夹角不等于90度。
实施例六
与实施例一相同，泄压槽为一条。与实施例一的区别在于，泄压槽的形状与实施例一是不同的。
在图14所示的具体实施例中，泄压槽为一条且呈环形。
实施例七
与实施例一的区别在于，泄压槽的个数与实施例一是不同的。
在图15所示的具体实施例中，泄压槽为两条且呈十字形。
实施例八
与实施例七相同，泄压槽为多条。与实施例七的区别在于，泄压槽的形状是不同的。
在图16所示的具体实施例中，泄压槽为三条且呈H形。
当然，三条泄压槽的组合也可以呈“工”字形。
实施例九
与实施例七相同，泄压槽为多条。与实施例七的区别在于，泄压槽的形状是不同的。
在图17所示的具体实施例中，泄压槽为多条且呈鱼骨形。
实施例十
与实施例七相同，泄压槽为多条。与实施例七的区别在于，泄压槽的形状是不同的。
在图18所示的具体实施例中，泄压槽为两条，且第一条泄压槽沿活塞1的周向或者气缸4的周向延伸，第二条泄压槽呈环状并与第一条泄压槽交叉。
在上述本公开实施例中，活塞套位于气缸内，且活塞的外周壁与气缸的内壁之间形成压缩腔，活塞的外周壁或气缸的内壁上对应于压缩腔的位置设置有泄压凹部。当泵体组件处于排气过程中时，远离排气口的气体能够通过泄压凹部向排气口处流动，增大了排气面积，进一步地改善了泵体组件在排气时出现过压缩的情况。
显然，上述所描述的实施例仅仅是本公开一部分的实施例，而不是全部的实施例。基于本公开中的实施例，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，都应当属于本公开保护的范围。
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公开的示例性实施方式。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，本公开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，以便这里描述的本公开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。
以上仅为本公开的优选实施例而已，并不用于限制本公开，对于本领域的技术人员来说，本公开可以有各种更改和变化。凡在本公开的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本公开的保护范围之内。

Claims (18)

  1. 一种泵体组件，包括：
    活塞(1)；
    转轴(2)；
    活塞套(3)，所述转轴(2)驱动所述活塞(1)在转动的同时在所述活塞套(3)内往复运动；
    气缸(4)，所述活塞套(3)位于所述气缸(4)内，且所述活塞(1)的外周壁与所述气缸(4)的内壁之间形成压缩腔(5)，所述活塞(1)的外周壁或所述气缸(4)的内壁上对应于所述压缩腔(5)的位置设置有泄压凹部(11)。
  2. 根据权利要求1所述的泵体组件，其中，在运动的过程中，所述活塞(1)的外周壁除所述泄压凹部(11)所在的位置的其他部分能够与所述气缸(4)的内壁适配。
  3. 根据权利要求1所述的泵体组件，其中，所述泄压凹部(11)沿所述活塞(1)的周向延伸。
  4. 根据权利要求3所述的泵体组件，其中，所述泄压凹部(11)沿所述活塞(1)的旋转方向的两端分别距离所述压缩腔(5)相应两端的弧长之和大于等于2毫米。
  5. 根据权利要求3所述的泵体组件，其中，所述气缸(4)还具有排气通道(41)，所述泄压凹部(11)沿所述活塞(1)的旋转方向的两端中靠近所述排气通道(41)的一端与所述排气通道(41)之间的弧长大于等于1毫米。
  6. 根据权利要求1所述的泵体组件，其中，
    在所述转轴(2)的轴线方向上，所述泄压凹部(11)与所述活塞(1)的边缘之间的距离大于等于1毫米；或
    在所述转轴(2)的轴线方向上，所述泄压凹部(11)与所述气缸(4)的边缘之间的距离大于等于1毫米。
  7. 根据权利要求1所述的泵体组件，其中，所述泄压凹部(11)包括至少一条泄压槽，当所述泄压槽为多个时，多个所述泄压槽彼此连通或彼此独立。
  8. 根据权利要求7所述的泵体组件，其中，各所述泄压槽的槽宽大于等于0.5毫米。
  9. 根据权利要求7所述的泵体组件，其中，各所述泄压槽的槽深大于等于0.1毫 米。
  10. 根据权利要求7所述的泵体组件，其中，所有所述泄压槽的横截面积大于等于0.025平方毫米。
  11. 根据权利要求7所述的泵体组件，其中，所有所述泄压槽的横截面积之和与所述活塞(1)沿垂直于所述气缸(4)轴线的横截面积的比值大于等于0.001且小于等于0.5。
  12. 根据权利要求7所述的泵体组件，其中，各所述泄压槽的横截面为矩形或者扇形。
  13. 根据权利要求7所述的泵体组件，其中，
    所述泄压槽为一条且沿所述活塞(1)的周向或者所述气缸(4)的周向延伸；或者
    所述泄压槽为两条且呈十字形；或者
    所述泄压槽为三条且呈H形；或者
    所述泄压槽为三条且呈“工”字形；或者
    所述泄压槽为多条且呈鱼骨形；或者
    所述泄压槽为两条，且第一条所述泄压槽沿所述活塞(1)的周向或者所述气缸(4)的周向延伸，第二条所述泄压槽呈环状并与第一条所述泄压槽交叉。
  14. 根据权利要求1至13中任一项所述的泵体组件，其中，所述泄压凹部(11)的凹腔体积与所述泵体组件的排量之比大于等于0.001且小于等于0.02。
  15. 一种流体机械，包括权利要求1至14中任一项所述的泵体组件。
  16. 根据权利要求15所述的流体机械，其中，所述流体机械是压缩机。
  17. 一种换热设备，包括权利要求15或16所述的流体机械。
  18. 一种流体机械的运转方法，其中，所述流体机械是权利要求15或16所述的流体机械，所述流体机械的气缸(4)具有间隔设置的吸气通道(43)、泄压通道(42)和排气通道(41)，且所述泄压通道(42)与所述气缸(4)的腔体通过泄压口连通，所述排气通道(41)与所述气缸(4)的腔体通过排气口连通，所述运转方法包括：
    在所述流体机械处于排气结束时，所述流体机械的泵体组件的泄压凹部(11)直接或间接地与所述泄压口连通，同时与所述排气口脱离。
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