WO2023103876A1 - 流体机械和换热设备 - Google Patents

流体机械和换热设备 Download PDF

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Publication number
WO2023103876A1
WO2023103876A1 PCT/CN2022/135956 CN2022135956W WO2023103876A1 WO 2023103876 A1 WO2023103876 A1 WO 2023103876A1 CN 2022135956 W CN2022135956 W CN 2022135956W WO 2023103876 A1 WO2023103876 A1 WO 2023103876A1
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WO
WIPO (PCT)
Prior art keywords
fluid machine
machine according
cylinder liner
exhaust
crankshaft
Prior art date
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PCT/CN2022/135956
Other languages
English (en)
French (fr)
Inventor
徐嘉
杜忠诚
于瑞波
李直
张培林
宋雪威
Original Assignee
珠海格力电器股份有限公司
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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
Publication of WO2023103876A1 publication Critical patent/WO2023103876A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • 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
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • 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
    • F25B31/00—Compressor arrangements

Definitions

  • the present disclosure relates to the technical field of heat exchange systems, in particular, to fluid machinery and heat exchange equipment.
  • Fluid machines in the related art known to the inventor include compressors, expanders, and the like.
  • a fluid machine including two flanges, a crankshaft, a cylinder liner, a cross groove structure and two sliders, wherein the crankshaft is provided with two Eccentric part, there is a phase difference of the first angle A between the two eccentric parts; the crankshaft and the cylinder liner are arranged eccentrically and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder liner, and the cross groove structure has two limit positions channel, two limiting channels are arranged in sequence along the axial direction of the crankshaft, the extending direction of the limiting channel is perpendicular to the axial direction of the crankshaft, and there is a phase difference of the second angle B between the extending directions of the two limiting channels, Among them, the first included angle A is twice the second included angle B; the slider has a through hole, and there are two sliders, the crankshaft passes through the two flanges and the cylinder liner
  • variable volume cavity is located in the sliding direction of the slider, and the crankshaft is configured to drive the slider through rotation. Sliding reciprocally in the limiting channel and interacting with the intersecting groove structure at the same time, so that the intersecting groove structure and the slider rotate in the cylinder liner.
  • the end face of at least one end of the intersecting groove structure is open, and the limiting channel on one side of the opening is directly penetrated to the end face along the axial direction of the intersecting groove structure, and the intersecting groove structure is far away from the open end.
  • the end surface of one end is reserved with an opening for the crankshaft to protrude, the opening is arranged concentrically with the intersecting groove structure, and the opening communicates with the limiting channel.
  • holes are reserved on the end surfaces of both ends of the intersecting groove structure for the extension of the crankshaft, the openings are arranged concentrically with the intersecting groove structure, and the openings communicate with the limiting passage.
  • crankshaft is concentric with the flange.
  • first assembly gap between the crankshaft and the flange, and the range of the first assembly gap is 0.005mm ⁇ 0.05mm.
  • the first assembly gap ranges from 0.01 mm to 0.03 mm.
  • the eccentricity of the eccentric part is equal to the assembly eccentricity of the crankshaft and the cylinder liner.
  • both ends of the limiting channel penetrate to the outer peripheral surface of the intersecting groove structure.
  • the two sliders are arranged concentrically with the two eccentric parts respectively, and the sliders make circular motions around the axis of the crankshaft.
  • the intersecting groove structure is arranged coaxially with the cylinder liner, and there is a second rotation gap between the outer peripheral surface of the intersecting groove structure and the inner wall surface of the cylinder liner, and the size of the second rotation gap ranges from 0.005 mm to 0.1 mm.
  • the range of the first included angle A is 160°-200°; the range of the second included angle B is 80°-100°.
  • the eccentric part has an arc surface, the arc surface is coaxially arranged with the crankshaft, and the central angle of the arc surface is greater than or equal to 180 degrees.
  • the eccentric portion is cylindrical.
  • the proximal end of the eccentric portion is flush with the outer circle of the shaft portion of the crankshaft; or, the proximal end of the eccentric portion protrudes from the outer circle of the shaft portion of the crankshaft; or, the proximal end of the eccentric portion is located on the crankshaft The inner side of the outer circle of the shaft part; wherein, the proximal end is the position on the outer side of the eccentric part with the smallest distance from the axis of the crankshaft.
  • the two eccentric portions are arranged at intervals in the axial direction of the crankshaft.
  • the intersecting groove structure has a central hole through which the two limiting passages communicate, and the diameter of the central hole is larger than the diameter of the crankshaft shaft body.
  • the diameter of the central hole is larger than the diameter of the eccentric portion.
  • the position-limiting channel has a set of opposite first sliding surfaces that are in sliding contact with the slider, the slider has a second sliding surface that cooperates with the first sliding surfaces, and the slider has a The extrusion surface at the end of the channel serves as the head of the slider, the two second sliding surfaces are connected through the extrusion surface, and the extrusion surface faces the variable volume cavity.
  • the extrusion surface is an arc surface, and the distance between the arc center of the arc surface and the center of the through hole is equal to the eccentricity of the eccentric portion.
  • the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner; or, there is a difference between the radius of curvature of the arc surface and the radius of the inner circle of the cylinder liner, and the difference ranges from -0.05mm to 0.025 mm.
  • the difference ranges from -0.02 to 0.02 mm.
  • the shape of the slider on the cross-section of the limiting channel matches the shape of the cross-section of the limiting channel.
  • the projection of the slider on the sliding direction of the slider is a square, and the ratio range between the width W of the square and the height H of the square satisfies: 0.5-3.
  • the ratio of the width W of the square to the height H of the square satisfies: 1.5 ⁇ 2.5.
  • the cross-section of the limiting channel is a part of a semicircle
  • the projection of the slider on the sliding direction of the slider includes an arc segment and a straight line segment, and twice the radius of curvature of the arc segment is D1, and the straight line
  • the length of the segment is d1, and the relationship between D1 and d1 satisfies: the ratio of d1/D1 ranges from 0.3 to 1.
  • the relationship between D1 and d1 satisfies: the ratio of d1/D1 ranges from 0.5 to 0.7.
  • the cylinder liner has a compression intake port and a compression exhaust port.
  • the compression intake port When any slider is in the intake position, the compression intake port is connected to the corresponding variable volume chamber; In the case of the air position, the corresponding variable volume chamber is connected to the compression exhaust port.
  • the projected area of the extrusion surface in the sliding direction of the slider is the S slider
  • the exhaust area of the compression exhaust port of the cylinder liner is the S row
  • the ratio of the S slider /S row is in the range of 8- 25.
  • the ratio of S sliders /S rows is in the range of 12-18.
  • the inner wall of the cylinder liner has an air suction chamber, and the air suction chamber communicates with the compressed air inlet.
  • the suction cavity extends a first preset distance around the inner wall surface of the cylinder liner to form an arc-shaped suction cavity.
  • the two suction cavities are arranged at intervals along the axial direction of the cylinder liner, the cylinder liner also has a suction communication cavity, both of the two suction cavities communicate with the suction communication cavity, and The compressed air inlet communicates with the suction cavity through the suction communication cavity.
  • the suction communication cavity extends a second preset distance along the axial direction of the cylinder liner, and at least one end of the suction communication cavity passes through the axial end surface of the cylinder liner.
  • an exhaust cavity is opened on the outer wall of the cylinder liner, and the compressed exhaust port is connected to the exhaust cavity by the inner wall of the cylinder liner.
  • the fluid machine also includes an exhaust valve assembly, which is arranged on the exhaust The cavity is set correspondingly to the compression exhaust port.
  • a communication hole is provided on the axial end surface of the cylinder liner, and the communication hole communicates with the exhaust cavity.
  • the fluid machine also includes a flange, and an exhaust passage is arranged on the flange, and the communication hole communicates with the exhaust passage. .
  • the exhaust cavity penetrates to the outer wall of the cylinder liner, and the fluid machine further includes an exhaust cover plate, which is connected with the cylinder liner and seals the exhaust cavity.
  • the fluid machine is a compressor.
  • the cylinder liner has an expansion exhaust port and an expansion intake port.
  • the expansion exhaust port When any slider is in the intake position, the expansion exhaust port is connected to the corresponding variable volume chamber; In the case of the air position, the corresponding variable volume chamber is connected to the expansion air inlet.
  • the inner wall of the cylinder liner has an expansion exhaust cavity, and the expansion exhaust cavity communicates with the expansion exhaust port.
  • the expansion exhaust cavity extends a first preset distance around the inner wall surface of the cylinder liner to form an arc-shaped expansion exhaust cavity, and the expansion exhaust cavity extends from the expansion exhaust port to the expansion intake The side where the port is located extends, and the extension direction of the expansion exhaust cavity is in the same direction as the rotation direction of the intersecting groove structure.
  • the two expansion exhaust chambers are arranged at intervals along the axial direction of the cylinder liner.
  • the communication cavity communicates, and the expansion exhaust port communicates with the expansion exhaust cavity through the expansion exhaust communication cavity.
  • the expansion exhaust communication cavity extends a second preset distance along the axial direction of the cylinder liner, and at least one end of the expansion exhaust communication cavity passes through the axial end surface of the cylinder liner.
  • the fluid machine is an expander.
  • a heat exchange device including the fluid machine of the above embodiment.
  • Fig. 1 shows a schematic diagram of a mechanism for the operation of a compressor according to some embodiments of the present disclosure
  • Fig. 2 shows a schematic diagram of the principle of operation of the compressor in Fig. 1;
  • FIG. 3 shows a schematic diagram of the internal structure of a compressor according to Embodiment 1 of the present disclosure
  • Fig. 4 shows a schematic structural view of the pump body assembly of the compressor in Fig. 3;
  • Figure 5 shows a schematic diagram of the exploded structure of the pump body assembly in Figure 4.
  • Fig. 6 shows the schematic diagram of the assembly structure of crankshaft, intersecting groove structure, slide block in Fig. 5;
  • Fig. 7 shows the schematic cross-sectional structure diagram of the crankshaft, the intersecting groove structure and the slide block in Fig. 6;
  • FIG. 8 shows a schematic structural diagram of the cross-groove structure in FIG. 5;
  • Fig. 9 shows a schematic structural view of the slider in Fig. 5;
  • Fig. 10 shows a schematic structural view of the shaft body part and two eccentric parts of the crankshaft in Fig. 5;
  • Fig. 11 shows a structural schematic diagram of the shaft body part of the crankshaft in Fig. 10 and the eccentricity of the two eccentric parts;
  • Fig. 12 shows the sectional structure schematic diagram of the assembly eccentricity of crankshaft and cylinder liner in Fig. 4;
  • Fig. 13 shows a schematic structural view of the cylinder liner and the lower flange in Fig. 5 when they are in an exploded state;
  • Fig. 14 shows a schematic structural view of the eccentricity between the cylinder liner and the lower flange in Fig. 13;
  • Fig. 15 shows a schematic structural view of the slider in Fig. 9 in the axial direction of the through hole
  • Figure 16 shows a schematic structural view of the cylinder liner in Figure 13;
  • Fig. 17 shows a structural schematic diagram of another viewing angle of the cylinder liner in Fig. 16;
  • Fig. 18 shows a schematic cross-sectional structural view of the cylinder liner in Fig. 17;
  • Fig. 19 shows a schematic cross-sectional structural view of another viewing angle of the cylinder liner in Fig. 17;
  • Fig. 20 shows a schematic view of the structure of the Y-direction viewing angle in Fig. 19;
  • Fig. 21 shows a schematic cross-sectional view of the upper flange and the cylinder liner in Fig. 12, in which the exhaust path of the pump body assembly is shown;
  • Fig. 22 shows a schematic cross-sectional structural view of the exhaust path of the pump body assembly in Fig. 4;
  • Fig. 23 shows a schematic structural view of the cylinder liner and exhaust cover plate in Fig. 5 when they are in an exploded state;
  • Fig. 24 shows a schematic diagram of the state structure of the compressor in Fig. 3 at the beginning of suction
  • Fig. 25 shows a schematic diagram of the state structure of the compressor in Fig. 3 in the suction process
  • Fig. 26 shows a schematic diagram of the state structure of the compressor in Fig. 3 at the end of suction
  • Fig. 27 shows a schematic diagram of the state structure of the compressor in Fig. 3 when it is compressing gas
  • Fig. 28 shows a schematic diagram of the state structure of the compressor in Fig. 3 in the exhaust process
  • Fig. 29 shows a schematic diagram of the state structure of the compressor in Fig. 3 at the end of exhaust
  • Figure 30 shows a schematic cross-sectional structural view of the pump body assembly with bearings in Figure 3, in which the bearing is located at one axial end;
  • Figure 31 shows a schematic structural view of the intersecting groove structure and the bearing in Figure 30 when they are in an assembled state
  • Figure 32 shows a schematic cross-sectional structural view of the pump body assembly with bearings in Figure 3, in which the bearings are located at both axial ends;
  • Figure 33 shows a schematic structural view of the intersecting groove structure and the bearing in Figure 32 when they are in an assembled state
  • Figure 34 shows a schematic cross-sectional structural view of the pump body assembly with bearings in Figure 3, in which the bearing is located at the other end in the axial direction;
  • Fig. 35 shows a schematic structural view of the intersecting groove structure and the bearing in Fig. 34 when they are in an assembled state
  • Fig. 36 shows a schematic cross-sectional structural view of the pump body assembly with bearings in Fig. 3, in which the bearings are located on the circumferential outer peripheral side;
  • Fig. 37 shows a schematic structural view of the cylinder liner, intersecting groove structure and bearing in Fig. 36 when they are in an assembled state;
  • Fig. 38 shows a schematic cross-sectional structural view of the pump body assembly with bearings in Fig. 3, in this figure, the bearings are located between the two sub-cylinder sleeves;
  • Fig. 39 shows a structural schematic view of the intersecting groove structure and the bearing in Fig. 38 when they are in an assembled state
  • Fig. 40 shows a schematic diagram of the structure of the intersecting groove structure in Fig. 3 and the cross section of the slider being elliptical;
  • Fig. 41 shows a schematic structural diagram of the intersecting groove structure and the cross section of the slider in Fig. 3;
  • Fig. 42 shows a schematic diagram of the structure of the intersecting groove structure and the cross section of the slider in Fig. 3 being trapezoidal;
  • Fig. 43 shows a schematic diagram of the structure of the intersecting groove structure in Fig. 3 and the cross section of the slider being circular;
  • Fig. 44 shows a schematic diagram of the internal structure of a compressor according to Embodiment 2 of the present disclosure
  • Figure 45 shows a schematic structural view of the pump body assembly of the compressor in Figure 44;
  • Fig. 46 shows a schematic structural view of the intersecting groove structure of the pump body assembly in Fig. 45;
  • Fig. 47 shows a schematic diagram of the internal structure of a compressor according to Embodiment 3 of the present disclosure
  • Figure 48 shows a schematic structural view of the pump body assembly of the compressor in Figure 47;
  • Fig. 49 shows a schematic structural view of the intersecting groove structure of the pump body assembly in Fig. 47;
  • Fig. 50 shows a schematic diagram of the mechanism principle of compressor operation in the related art
  • Figure 51 shows a schematic diagram of the mechanism principle of the improved compressor operation in the related art
  • Fig. 52 shows a schematic diagram of the operating mechanism of the compressor in Fig. 51. In this figure, the force arm of the drive shaft driving the slider to rotate is shown;
  • Fig. 53 shows a schematic diagram of the operating mechanism of the compressor in Fig. 51.
  • the center of the limiting groove structure coincides with the center of the eccentric part.
  • Dispenser component 81. Housing assembly; 82. Motor assembly; 83. Pump body assembly; 84. Upper cover assembly; 85. Lower cover assembly;
  • a compressor operating mechanism principle is proposed based on the cross slider mechanism, that is, point O1 is used as the center of the cylinder, point O2 is used as the center of the drive shaft, and point O3 is used as the center of the slider ,
  • the cylinder and the drive shaft are set eccentrically, and the center O 3 of the slider makes a circular motion on a circle with a diameter of O 1 O 2 .
  • the cylinder center O 1 and the drive shaft center O 2 are used as the two rotation centers of the motion mechanism, and at the same time, the midpoint O 0 of the line segment O 1 O 2 is used as the virtual center of the slider center O 3 , so that the slider While the block reciprocates relative to the cylinder, the slider also reciprocates relative to the drive shaft.
  • a The motion mechanism with O 0 as the drive shaft center that is, the cylinder center O 1 and the drive shaft center O 0 as the two rotation centers of the motion mechanism, the drive shaft has an eccentric portion, the slider and the eccentric portion are coaxially arranged, and the drive shaft and The assembly eccentricity of the cylinder is equal to the eccentricity of the eccentric part, so that the slider center O3 makes a circular motion with the drive shaft center O0 as the center and O1O0 as the radius .
  • a set of operating mechanisms including a cylinder, a limit groove structure, a slider and a drive shaft, wherein the limit groove structure is rotatably arranged in the cylinder, and the cylinder and the limit groove structure are coaxially arranged, that is, The center O1 of the cylinder is also the center of the limit groove structure, the slider reciprocates relative to the limit groove structure, the slider is coaxially assembled with the eccentric portion of the drive shaft, and the slider moves circularly around the shaft part of the drive shaft, specifically The movement process is: the drive shaft rotates, driving the slider to revolve around the center of the shaft part of the drive shaft, the slider rotates relative to the eccentric part at the same time, and the slider reciprocates in the limit groove of the limit groove structure, and pushes the limit Bitslot structure rotation.
  • the present disclosure proposes a mechanism principle of a cross groove structure with two limiting channels and double sliders, and builds a fluid machine such as a compressor and an expander based on this principle, and the fluid machine has high energy efficiency , low noise, the following will take the compressor as an example to introduce the compressor based on the cross-groove structure with two limiting channels and double sliders.
  • the present disclosure provides a fluid machine and heat exchange equipment, wherein the heat exchange equipment includes the following fluid machine.
  • the first angle A between the two eccentric parts is the first angle A between the extension directions of the two limiting passages Two times the included angle B, so that when one of the two sliders is at the dead point position, that is, the driving torque of the eccentric part corresponding to the slider at the dead point position is 0, and it is at the dead point position
  • the slider at the position cannot continue to rotate, and at this time the driving torque of the other eccentric part of the two eccentric parts driving the corresponding slider is the maximum value, ensuring that the eccentric part with the largest driving torque can normally drive the corresponding slider Rotate, so that the cross groove structure is driven to rotate through the slider, and then the slider at the dead point is driven to continue to rotate through the cross groove structure, realizing the stable operation of the fluid machine, avoiding the dead point position of the movement mechanism, and lifting It improves the motion reliability of the fluid machinery, thus ensuring the working reliability of the heat exchange equipment.
  • the crankshaft passes through the two flanges and the cylinder liner to ensure that the two flanges can limit the cylinder liner, thereby ensuring that the cylinder Set of installation reliability.
  • fluid machinery such as compressors and expanders can be ensured to have high energy efficiency and low noise, thereby ensuring the reliability of the heat exchange equipment.
  • the fluid machine in the present disclosure includes two flanges 50, a crankshaft 10, a cylinder liner 20, a cross groove structure 30 and two sliders 40, wherein the crankshaft 10 is provided with two eccentrics along its axial direction.
  • the crankshaft 10 and the cylinder liner 20 are set eccentrically and the eccentric distance is fixed;
  • the cross groove structure 30 is rotatably arranged in the cylinder liner 20, and the cross groove structure 30 has two limiting passages 31, the two limiting passages 31 are arranged in sequence along the axial direction of the crankshaft 10, the extending direction of the limiting passages 31 is perpendicular to the axial direction of the crankshaft 10, and the extending direction of the two limiting passages 31
  • the second included angle B wherein the first included angle A is twice the second included angle B;
  • the slider 40 has a through hole 41, there are two sliders 40, and the crankshaft 10 passes through two The flange 50 and the cylinder liner 20, and the two eccentric parts 11 correspondingly protrude into the two through holes 41 of the two sliders 40, and the two sliders 40 are correspondingly slidably arranged in the two limiting passages 31 to form a
  • the two eccentric parts 11 of the crankshaft extend into the two through holes 41 of the two sliders 40 correspondingly.
  • the two sliders 40 are correspondingly slidably arranged in the two limiting passages 31 to form a variable volume cavity 311, since the first angle A between the two eccentric parts 11 is the extension direction of the two limiting passages 31 Twice the second included angle B between them, so that when one of the two sliders 40 is at the dead point position, that is, the driving torque of the eccentric portion 11 corresponding to the slider 40 at the dead point position is 0, the slider 40 at the dead point cannot continue to rotate, and at this time, the driving torque of the other eccentric part 11 driving the corresponding slider 40 in the two eccentric parts 11 is the maximum value, ensuring the maximum driving torque.
  • the eccentric portion 11 of the moment can normally drive the corresponding slider 40 to rotate, thereby driving the cross groove structure 30 to rotate through the slider 40, and then driving the slider 40 at the dead point to continue to rotate through the cross groove structure 30, realizing
  • the stable operation of the fluid machinery avoids the dead point position of the motion mechanism, improves the movement reliability of the fluid machinery, and ensures the working reliability of the heat exchange equipment.
  • fluid machinery such as compressors and expanders can be ensured to have high energy efficiency and low noise, thereby ensuring the reliability of the heat exchange equipment.
  • neither the first included angle A nor the second included angle B is zero.
  • the crankshaft 10 rotates around the axis O 0 of the crankshaft 10; the intersecting groove structure 30 revolves around the axis O 0 of the crankshaft 10, and the axis O 0 Set eccentrically with the axis O 1 of the intersecting groove structure 30 and the eccentric distance is fixed; the first slider 40 makes a circular motion with the axis O 0 of the crankshaft 10 as the center of a circle, and the center O 3 of the first slider 40 is aligned with the crankshaft
  • the distance between the axis O0 of 10 is equal to the eccentricity of the first eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentricity between the axis O0 of the crankshaft 10 and the axis O1 of the intersecting groove structure 30 distance, the crankshaft 10 rotates to drive the first slider 40 to make a circular motion, and the first slider 40 interacts with the intersecting groove structure 30 and slides reciproc
  • the fluid machine operated as described above constitutes an Oldham slider mechanism, and the operation method adopts the principle of the Oldham slider mechanism, wherein the two eccentric parts 11 of the crankshaft 10 serve as the first connecting rod L1 and the second connecting rod L2 respectively. , the two limiting channels 31 of the intersecting groove structure 30 are respectively used as the third link L 3 and the fourth link L 4 , and the lengths of the first link L 1 and the second link L 2 are equal (please refer to FIG. 1 ).
  • first included angle A between the first link L1 and the second link L2
  • second included angle B between the third link L3 and the fourth link L4
  • first included angle A is twice the second included angle B
  • the line connecting the axis O 0 of the crankshaft 10 and the axis O 1 of the intersecting groove structure 30 is the line O 0 O 1 , and the line between the first connecting rod L 1 and the line O 0 O 1
  • There is a fifth included angle E between the second connecting rod L 2 and the connecting line O 0 O 1 and there is a sixth included angle F between the corresponding fourth connecting rod L 4 and the connecting line O 0 O 1 , wherein the fifth included angle
  • the angle E is twice the sixth angle F;
  • the sum of the third angle C and the fifth angle E is the first angle A, and the sum of the fourth angle D and the sixth angle F is the second angle b.
  • the operation method further includes that the rotational angular velocity of the slider 40 relative to the eccentric portion 11 is the same as the revolution angular velocity of the slider 40 around the axis O 0 of the crankshaft 10 ;
  • the revolution angular velocity is the same as the rotation angular velocity of the slider 40 relative to the eccentric portion 11 .
  • the axis O0 of the crankshaft 10 corresponds to the rotation center of the first connecting rod L1 and the second connecting rod L2
  • the axis O1 of the intersecting groove structure 30 corresponds to the third connecting rod L3 and the fourth connecting rod L3 .
  • the rotation center of the connecting rod L4 ; the two eccentric parts 11 of the crankshaft 10 are respectively used as the first connecting rod L1 and the second connecting rod L2 , and the two limiting channels 31 of the intersecting groove structure 30 are respectively used as the third connecting rod L 3 and the fourth connecting rod L 4 , and the lengths of the first connecting rod L 1 and the second connecting rod L 2 are equal, so that when the crankshaft 10 rotates, the eccentric part 11 on the crankshaft 10 drives the corresponding slider 40 around the crankshaft
  • the axis O0 of 10 revolves, and the slider 40 can rotate relative to the eccentric part 11 at the same time, and the relative rotation speed of the two is the same, because the first slider 40 and the second slider 40 are respectively in two corresponding limits Reciprocating movement in the position channel 31, and drives the intersecting groove structure 30 to make a circular motion, limited by the two limiting channels 31 of the intersecting groove structure 30, the moving direction of the two sliders 40 always has the phase of the second included angle B difference, when one of the two sliders
  • the maximum moment arm of the driving torque of the eccentric portion 11 is 2e.
  • the running track of the slider 40 is a circle, and the circle takes the axis O 0 of the crankshaft 10 as the center and the connecting line O 0 O 1 as the radius.
  • crankshaft 10 rotates 2 times to complete 4 intake and exhaust processes.
  • the end faces of both ends of the intersecting groove structure 30 are reserved with openings 38 for the crankshaft 10 to protrude.
  • the openings 38 are concentrically arranged with the intersecting groove structure 30. 31 connected. In this way, while ensuring that the crankshaft 10 can smoothly pass through the intersecting groove structure 30 , when the intersecting groove structure 30 is located in the cylinder liner 20 , the cylinder liner 20 can be well sealed.
  • the fluid machine also includes a flange 50, the flange 50 is arranged on the axial end of the cylinder liner 20, the crankshaft 10 is concentrically arranged with the flange 50, and the intersecting groove structure 30 is concentric with the cylinder liner 20.
  • the assembly eccentricity of the crankshaft 10 and the intersecting groove structure 30 is determined by the relative positional relationship between the flange 50 and the cylinder liner 20, wherein the flange 50 is fixed on the cylinder liner 20 by a fastener 90, and the axis center of the flange 50
  • the relative position of the axis of the inner ring of the cylinder liner 20 is controlled by the alignment of the flange 50, and the relative position of the axis of the flange 50 and the axis of the inner ring of the cylinder liner 20 determines the axis of the crankshaft 10 and the cross groove structure 30
  • the relative position of the shaft center, the essence of adjusting the center through the flange 50 is to make the eccentricity of the eccentric part 11 equal to the assembly eccentricity of the crankshaft 10 and the cylinder liner 20 .
  • the eccentricity of the two eccentric parts 11 is equal to e, and as shown in FIG. 20 are coaxially arranged, the assembly eccentricity between the crankshaft 10 and the intersecting groove structure 30 is the assembly eccentricity between the crankshaft 10 and the cylinder liner 20), and the flange 50 includes an upper flange 52 and a lower flange 53, as shown in Figure 14
  • the distance between the axis of the inner ring of the cylinder liner 20 and the axis of the inner ring of the lower flange 53 is e, which is equal to the eccentricity of the eccentric portion 11 .
  • first assembly gap between the crankshaft 10 and the flange 50, and the range of the first assembly gap is 0.005mm ⁇ 0.05mm.
  • the first assembly gap ranges from 0.01 mm to 0.03 mm.
  • both ends of the limiting channel 31 penetrate to the outer peripheral surface of the intersecting groove structure 30 . In this way, it is beneficial to reduce the manufacturing difficulty of the intersecting groove structure 30 .
  • the two sliders 40 are arranged concentrically with the two eccentric parts 11 respectively, the sliders 40 make a circular motion around the axis of the crankshaft 10, and there is a first rotation between the wall of the through hole 41 and the eccentric parts 11.
  • the gap, the range of the first rotation gap is 0.005mm-0.05mm.
  • the intersecting groove structure 30 is arranged coaxially with the cylinder liner 20, and there is a second rotation gap between the outer peripheral surface of the intersecting groove structure 30 and the inner wall surface of the cylinder liner 20, and the size of the second rotation gap is 0.005 mm to 0.1 mm.
  • the shaft body part 12 of the crankshaft 10 is integrally formed, and the shaft body part 12 has only one shaft center. In this way, the one-time molding of the shaft part 12 is facilitated, thereby reducing the difficulty of manufacturing the shaft part 12 .
  • the shaft portion 12 of the crankshaft 10 includes a first section and a second section connected along its axial direction, the first section and the second section are arranged coaxially, Two eccentric portions 11 are respectively arranged on the first segment and the second segment.
  • the first segment is detachably connected to the second segment. In this way, ease of assembly and disassembly of the crankshaft 10 is ensured.
  • the shaft portion 12 of the crankshaft 10 and the eccentric portion 11 are integrally formed. In this way, one-shot forming of the crankshaft 10 is facilitated, thereby reducing the difficulty of manufacturing the crankshaft 10 .
  • the shaft portion 12 of the crankshaft 10 is detachably connected to the eccentric portion 11 . In this way, the installation and removal of the eccentric portion 11 is facilitated.
  • the range of the first included angle A is 160°-200°; the range of the second included angle B is 80°-100°. In this way, it only needs to satisfy the relationship that the first included angle A is twice the second included angle B.
  • the first included angle A is 160 degrees
  • the second included angle B is 80 degrees
  • the first included angle A is 165 degrees
  • the second included angle B is 82.5 degrees.
  • the first included angle A is 170 degrees, and the second included angle B is 85 degrees.
  • the first included angle A is 175 degrees
  • the second included angle B is 87.5 degrees
  • the first included angle A is 180 degrees
  • the second included angle B is 90 degrees
  • the first included angle A is 185 degrees
  • the second included angle B is 92.5 degrees.
  • the first included angle A is 190 degrees, and the second included angle B is 95 degrees.
  • the first included angle A is 195 degrees
  • the second included angle B is 97.5 degrees.
  • the eccentric portion 11 has an arc surface, the arc surface is coaxially arranged with the crankshaft 10 , and the central angle of the arc surface is greater than or equal to 180 degrees. In this way, it is ensured that the arc surface of the eccentric portion 11 can exert an effective driving force on the slider 40 , thereby ensuring the reliability of the movement of the slider 40 .
  • the eccentric portion 11 is cylindrical.
  • the proximal end of the eccentric portion 11 is flush with the outer circle of the shaft portion of the crankshaft 10 .
  • the proximal end of the eccentric portion 11 protrudes beyond the outer circle of the shaft portion of the crankshaft 10 .
  • the proximal end of the eccentric portion 11 is located inside the outer circle of the shaft portion of the crankshaft 10 .
  • the proximal end is the position where the distance between the outer surface of the eccentric portion 11 and the axis of the crankshaft 10 is the smallest.
  • the slider 40 includes a plurality of sub-sliders, and the plurality of sub-sliders are assembled to form a through hole 41 .
  • two eccentric portions 11 are arranged at intervals in the axial direction of the crankshaft 10 .
  • the cylinder liner 20 and the two sliders 40 ensuring the distance between the two eccentric parts 11 can provide an assembly space for the cylinder liner 20 to ensure the convenience of assembly.
  • the intersecting groove structure 30 has a central hole 32 through which the two limiting passages 31 communicate.
  • the diameter of the central hole 32 is larger than the diameter of the shaft portion of the crankshaft 10 . In this way, it is ensured that the crankshaft 10 can pass through the central hole 32 smoothly.
  • the diameter of the central hole 32 is larger than the diameter of the eccentric portion 11 . In this way, it is ensured that the eccentric portion 11 of the crankshaft 10 can smoothly pass through the central hole 32 .
  • the axial projection of the slider 40 on the through hole 41 has two relatively parallel straight line segments and an arc segment connecting the ends of the two straight line segments.
  • the limit channel 31 has a set of oppositely disposed first sliding surfaces S1 that are in sliding contact with the slider 40.
  • the slider 40 has a second sliding surface S2 that cooperates with the first sliding surfaces S1.
  • the extruding surface 42 at the end of the position channel 31 serves as the head of the slider 40
  • the two second sliding surfaces S2 are connected by the extruding surface 42
  • the extruding surface 42 faces the variable volume cavity 311 .
  • the projection of the second sliding surface S2 of the slider 40 in the axial direction of its through hole 41 is a straight line segment, and at the same time, the projection of the extrusion surface 42 of the slider 40 in the axial direction of its through hole 41 is an arc segment .
  • the extrusion surface 42 is an arc surface, and the distance between the arc center of the arc surface and the center of the through hole 41 is equal to the eccentricity of the eccentric portion 11 .
  • the center of the through hole 41 of the slider 40 is the O slider, and the distance between the arc centers of the two arc surfaces and the center of the through hole 41 is e, that is, the eccentricity of the eccentric portion 11, as shown in Fig. 12
  • the dotted line of X indicates the circle where the arc centers of the two arc surfaces are located.
  • the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20 .
  • the difference ranges from -0.02 to 0.02 mm.
  • the shape of the slider 40 on the section of the limiting channel 31 is adapted to the shape of the section of the limiting channel 31 . In this way, the sliding stability of the slider 40 in the limiting channel 31 is ensured.
  • the section of the limiting channel 31 is one of semicircle, circle, rectangle, ellipse, square and trapezoid.
  • the projection of the slider 40 on the sliding direction of the slider 40 is a square, and the ratio between the width W of the square and the height H of the square satisfies: 0.5-3.
  • the ratio of the width W of the square to the height H of the square satisfies: 1.5 ⁇ 2.5.
  • the section of the limiting channel 31 is a part of a semicircle
  • the projection of the slider 40 on the sliding direction of the slider 40 is composed of an arc segment and a straight line segment
  • the radius of curvature of the arc segment is twice The multiple is D1
  • the length of the straight line is d1
  • the relationship between D1 and d1 satisfies: the ratio of d1/D1 ranges from 0.3 to 1.
  • the relationship between D1 and d1 satisfies: the ratio of d1/D1 ranges from 0.5 to 0.7.
  • the projected area of the extrusion surface 42 in the sliding direction of the slider 40 is the S slider
  • the exhaust area of the compression exhaust port 22 of the cylinder liner 20 is the S row
  • the ratio of the S slider /S row The range is 8-25.
  • the ratio of S sliders /S rows is in the range of 12-18.
  • the fluid machine shown in this embodiment is a compressor.
  • the lower cover assembly 85 wherein the liquid separator part 80 is arranged on the outside of the housing assembly 81, the upper cover assembly 84 is assembled on the upper end of the housing assembly 81, the lower cover assembly 85 is assembled on the lower end of the housing assembly 81, and the motor assembly 82
  • Both the motor assembly 82 and the pump body assembly 83 are located inside the housing assembly 81 , wherein the motor assembly 82 is located above the pump body assembly 83 , or the motor assembly 82 is located below the pump body assembly 83 .
  • the pump body assembly 83 of the compressor includes the crankshaft 10 , the cylinder liner 20 , the intersecting groove structure 30 , the slider 40 , the upper flange 52 and the lower flange 53 .
  • the above components are connected by means of welding, shrink fitting, or cold pressing.
  • the assembly process of the entire pump body assembly 83 is as follows: the lower flange 53 is fixed on the cylinder liner 20, the two sliders 40 are respectively placed in the corresponding two limiting passages 31, and the two eccentric parts 11 of the crankshaft 10 respectively extend into the In the two through holes 41 of the corresponding two sliders 40, the assembled crankshaft 10, the cross groove structure 30 and the two sliders 40 are placed in the cylinder liner 20, and one end of the crankshaft 10 is installed on the lower flange 53 , the other end of the crankshaft 10 is set through the upper flange 52 , see FIG. 4 and FIG. 5 for details.
  • the closed space surrounded by the slider 40, the limiting channel 31, the cylinder liner 20 and the upper flange 52 (or the lower flange 53) is the variable volume chamber 311, and the pump body assembly 83 has four variable volume chambers 311 in total.
  • the crankshaft 10 rotates 2 revolutions, and a single variable volume chamber 311 completes one intake and exhaust process.
  • the crankshaft 10 rotates 2 revolutions, totaling Complete 4 suction and exhaust processes.
  • the sliding block 40 rotates relative to the cylinder liner 20 during the reciprocating movement in the limiting channel 31.
  • the sliding block 40 is clockwise from 0° to 180° During the rotation process, the variable volume chamber 311 increases.
  • the variable volume chamber 311 communicates with the suction chamber 23 of the cylinder liner 20.
  • the slider 40 rotates to 180 degrees, the variable volume chamber The volume of 311 reaches the maximum value, at this time, the variable volume chamber 311 is separated from the suction chamber 23, thereby completing the suction operation.
  • the slider 40 continues to rotate clockwise from 180° to 360° During the process, the variable volume chamber 311 decreases, and the slider 40 compresses the gas in the variable volume chamber 311.
  • the slider 40 rotates until the variable volume chamber 311 communicates with the compression exhaust port 22, and when the variable volume chamber 311
  • the exhaust valve plate 61 of the exhaust valve assembly 60 opens, and the exhaust operation starts until the compression ends and enters the next cycle.
  • Figures 24 to 29 the point marked with M is used as the reference point for the relative movement of the slider 40 and the crankshaft 10, and Figure 25 shows the process of the slider 40 rotating clockwise from 0° to 180°, the rotation of the slider 40 The angle is ⁇ 1, and the corresponding rotation angle of the crankshaft 10 is 2 ⁇ 1.
  • Fig. 27 shows that the slider 40 continues to rotate clockwise from 180° to 360°, and the rotation angle of the slider 40 is 180°+ ⁇ 2, corresponding to The crankshaft 10 rotates at an angle of 360°+2 ⁇ 2.
  • Figure 28 shows that the slider 40 continues to rotate clockwise from 180° to 360°, and the variable volume cavity 311 communicates with the compression exhaust port 22, and the slider 40 rotates
  • the angle is 180°+ ⁇ 3, and the corresponding rotation angle of the crankshaft 10 is 360°+2 ⁇ 3, that is, the slider 40 rotates once, and the corresponding crankshaft 10 rotates twice, wherein, ⁇ 1 ⁇ 2 ⁇ 3.
  • the cylinder liner 20 has a compression intake port 21 and a compression exhaust port 22, when any slider 40 is at the intake position, the compression intake port 21 and the compression exhaust port The corresponding variable volume cavity 311 is in conduction; when any slider 40 is in the exhaust position, the corresponding variable volume cavity 311 is in conduction with the compression exhaust port 22 .
  • the inner wall surface of the cylinder liner 20 has an air suction chamber 23 , and the air suction chamber 23 communicates with the compressed air inlet 21 .
  • the suction chamber 23 can store a large amount of gas, so that the variable volume chamber 311 can be fully suctioned, so that the compressor can take in enough air, and when the suction is insufficient, the stored gas can be supplied in time Give the variable volume chamber 311 to ensure the compression efficiency of the compressor.
  • the suction cavity 23 is a cavity formed by radially hollowing out the inner wall of the cylinder liner 20 , and there may be one suction cavity 23 or two upper and lower ones.
  • the suction cavity 23 extends a first preset distance around the inner wall surface of the cylinder liner 20 to form an arc-shaped suction cavity 23 . In this way, it is ensured that the volume of the suction chamber 23 is large enough to store a large amount of gas.
  • the suction communication cavity 24 extends a second preset distance along the axial direction of the cylinder liner 20 , and at least one end of the suction communication cavity 24 passes through the axial end surface of the cylinder liner 20 . In this way, it is convenient to open the suction communication cavity 24 from the end surface of the cylinder liner 20 , ensuring the convenience of processing the suction communication cavity 24 .
  • an exhaust cavity 25 is opened on the outer wall of the cylinder liner 20, and the compression exhaust port 22 is connected to the exhaust cavity 25 by the inner wall of the cylinder liner 20.
  • the fluid machine also includes an exhaust The valve assembly 60 , the exhaust valve assembly 60 is arranged in the exhaust cavity 25 and is arranged corresponding to the compression exhaust port 22 .
  • the exhaust cavity 25 is used to accommodate the exhaust valve assembly 60 , which effectively reduces the occupied space of the exhaust valve assembly 60 , makes the components reasonably arranged, and improves the space utilization rate of the cylinder liner 20 .
  • the exhaust valve assembly 60 is connected to the cylinder liner 20 through a fastener 90, the exhaust valve assembly 60 includes an exhaust valve plate 61 and a valve plate baffle 62, and the exhaust valve plate 61 is arranged in the exhaust cavity 25 and cover the corresponding compression exhaust port 22, the valve plate baffle 62 is overlapped on the exhaust valve plate 61. In this way, the setting of the valve plate baffle 62 effectively prevents the excessive opening of the exhaust valve plate 61 , thereby ensuring the exhaust performance of the cylinder liner 20 .
  • fasteners 90 are screws.
  • a communication hole 26 is also arranged on the axial end face of the cylinder liner 20, and the communication hole 26 communicates with the exhaust chamber 25, and the fluid machine also includes a flange 50, the flange An exhaust channel 51 is provided on the 50 , and the communication hole 26 communicates with the exhaust channel 51 . In this way, the exhaust reliability of the cylinder liner 20 is ensured.
  • the exhaust cavity 25 penetrates to the outer wall of the cylinder liner 20 , and the fluid machine further includes an exhaust cover 70 , which is connected to the cylinder liner 20 and seals the exhaust cavity 25 .
  • the exhaust cover plate 70 plays a role of isolating the variable volume chamber 311 from the external space of the pump body assembly 83 .
  • variable volume chamber 311 communicates with the compression exhaust port 22
  • the exhaust valve plate 61 opens, and the compressed gas enters the exhaust chamber 25 through the compression exhaust port 22. and through the communication hole 26 on the cylinder liner 20, and then discharged through the exhaust passage 51 and enters the external space of the pump body assembly 83 (ie, the cavity of the compressor), thereby completing the exhaust process.
  • exhaust cover plate 70 is secured to cylinder liner 20 by fasteners 90 .
  • fasteners 90 are screws.
  • the outer contour of the exhaust cover 70 matches the outer contour of the exhaust cavity 25 .
  • the motor assembly 82 drives the crankshaft 10 to rotate, and the two eccentric parts 11 of the crankshaft 10 respectively drive the corresponding two sliders 40 to move.
  • the slider 40 revolves around the axis of the crankshaft 10, the slider 40 Relative to the eccentric part 11, the slider 40 reciprocates along the limiting channel 31, and drives the cross groove structure 30 to rotate in the cylinder liner 20.
  • the slider 40 reciprocates along the limiting channel 31 while revolving to form a cross slide Movement mode of the block mechanism.
  • the compressor can be used as an expander by exchanging the positions of the suction port and the exhaust port. That is, the exhaust port of the compressor is used as the suction port of the expander, and high-pressure gas is passed in, and other pushing mechanisms rotate, and the gas is discharged through the suction port of the compressor (exhaust port of the expander) after expansion.
  • the cylinder liner 20 When the fluid machine is an expander, the cylinder liner 20 has an expansion exhaust port and an expansion intake port. When any slider 40 is in the intake position, the expansion exhaust port is in communication with the corresponding variable volume chamber 311; When a slider 40 is in the exhaust position, the corresponding variable volume cavity 311 is in communication with the expansion inlet.
  • the inner wall of the cylinder liner 20 has an expansion exhaust cavity, and the expansion exhaust cavity communicates with the expansion exhaust port.
  • the expansion exhaust cavity extends a first preset distance around the inner wall surface of the cylinder liner 20 to form an arc-shaped expansion exhaust cavity, and the expansion exhaust cavity expands from the expansion exhaust port to the expansion inlet.
  • the side where the air port is located extends, and the extension direction of the expansion exhaust chamber is the same as the rotation direction of the intersecting groove structure 30 .
  • the two expansion exhaust chambers are arranged at intervals along the axial direction of the cylinder liner 20.
  • the cylinder liner 20 also has an expansion exhaust communication chamber, and the two expansion exhaust chambers are connected to the expansion
  • the exhaust communication cavity communicates, and the expansion exhaust port communicates with the expansion exhaust cavity through the expansion exhaust communication cavity.
  • the expansion exhaust communication cavity extends a second preset distance along the axial direction of the cylinder liner 20 , and at least one end of the expansion exhaust communication cavity passes through the axial end surface of the cylinder liner 20 .
  • the axial end of the intersecting groove structure 30 is sleeved with a bearing 200 , and is located above the axial end of the intersecting groove structure 30 .
  • bearings 200 are sheathed on both ends of the intersecting groove structure 30 in the axial direction.
  • the other axial end of the intersecting groove structure 30 is sleeved with a bearing 200 , and is located below one axial end of the intersecting groove structure 30 .
  • the bearing 200 is arranged in the cylinder liner 20 and the outer ring of the bearing 200 is attached to the inner wall of the cylinder liner 20, and the ratio between the height H1 of the bearing 200 and the height H2 of the cylinder liner 20 is defined at the same time Greater than 0.9 and less than 1.
  • the cylinder liner 20 includes two sub-cylinder liners 27, the bearing 200 is arranged between the two sub-cylinder liners 27, and the end faces of the two axial ends of the bearing 200 are respectively aligned with the two sub-cylinder liners 27 facing the bearing 200.
  • the end face of the side is fitted, and the bearing 200 is concentrically arranged with the two sub-cylinder sleeves 27.
  • the section of the limiting channel 31 is one of semicircle, circle, rectangle, ellipse, square and trapezoid.
  • the end surface of at least one end of the intersecting groove structure 30 is open, and the limiting passage 31 on one side of the open shape directly penetrates to the end surface along the axial direction of the intersecting groove structure 30, and the intersecting groove structure 30 is not in the end face of the open-shaped one end and reserves the opening 38 for the crankshaft 10 to protrude.
  • the structure 30 is arranged concentrically, and the opening 38 communicates with the limiting channel 31 .
  • one end of the intersecting groove structure 30 is open, and the open end is located above.
  • the difference between this embodiment and the third embodiment is that one end of the intersecting groove structure 30 is open, and the open end is located below.
  • Embodiment 1 Some technical solutions described in Embodiment 1, Embodiment 2, and Embodiment 3 above can be used for reference without causing conflicts.
  • spatially relative terms may be used here, such as “on !, “over !, “on the surface of !, “above”, etc., to describe The spatial positional relationship between one device or feature shown and other devices or features. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, devices described as “above” or “above” other devices or configurations would then be oriented “beneath” or “above” the other devices or configurations. under other devices or configurations”. Thus, the exemplary term “above” can encompass both an orientation of “above” and “beneath”. The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptions used herein interpreted accordingly.

Abstract

一种流体机械和换热设备。流体机械包括两个法兰（50）、曲轴（10）、缸套（20）、交叉槽结构（30）和两个滑块（40），曲轴（10）的两个偏心部（11）之间具有第一夹角A；曲轴（10）与缸套（20）偏心设置且偏心距离固定；交叉槽结构（30）可转动地设置在缸套（20）内，交叉槽结构（30）的两个限位通道（31）沿曲轴（10）的轴向顺次设置，两个限位通道（30）的延伸方向之间具有第二夹角B，第一夹角A为第二夹角B的二倍；两个偏心部（11）对应伸入两个滑块（40）的两个通孔（41）内。该流体机械改善了压缩机和膨胀机的能效较低、噪音较大的问题。

Description

流体机械和换热设备
相关申请的交叉引用
本公开是以申请号为202111489315.3，申请日为2021年12月7日的中国申请为基础，并主张其优先权，该中国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技术领域，具体而言，涉及一种流体机械和换热设备。
背景技术
发明人所知晓的相关技术中的流体机械包括压缩机和膨胀机等。
以压缩机为例，根据节能环保及消费者对空调舒适性要求，空调行业一直在追求高效和低噪。压缩机作为空调的心脏，对空调的能效和噪音水平有直接影响。滚动转子式压缩机作为主流的家用空调压缩机，经过近百年发展，已相对成熟，受结构原理限制，优化空间有限。若要取得重大突破，需从结构原理进行创新。
因此，需要提出一种具备能效高、噪音小等特点的流体机械例如压缩机和膨胀机。
发明内容
为了实现上述目的，根据本公开的一个方面，提供了一种流体机械，包括两个法兰、曲轴、缸套、交叉槽结构和两个滑块，其中，曲轴沿其轴向设置有两个偏心部，两个偏心部之间具有第一夹角A的相位差；曲轴与缸套偏心设置且偏心距离固定；交叉槽结构可转动地设置在缸套内，交叉槽结构具有两个限位通道，两个限位通道沿曲轴的轴向顺次设置，限位通道的延伸方向垂直于曲轴的轴向，且两个限位通道的延伸方向之间具有第二夹角B的相位差，其中，第一夹角A为第二夹角B的二倍；滑块具有通孔，滑块为两个，曲轴穿过两个法兰和缸套，且两个偏心部对应伸入两个滑块的两个通孔内，两个滑块对应滑动设置在两个限位通道内并形成变容积腔，变容积腔位于滑块的滑动方向上，曲轴被配置为通过转动带动滑块在限位通道内往复滑动，同时与交叉槽结构相互作用，使得交叉槽结构、滑块在缸套内转动。
在一些实施例中，交叉槽结构至少一端的端面呈敞口状，且呈敞口状一侧的限位通道沿交叉槽结构的轴向直接贯通至端面，交叉槽结构远离呈敞口状的一端的端面预 留有供曲轴伸出的开孔，开孔与交叉槽结构同心设置，开孔与限位通道连通。
在一些实施例中，交叉槽结构的两端的端面上均预留有供曲轴伸出的开孔，开孔与交叉槽结构同心设置，开孔与限位通道连通。
在一些实施例中，曲轴与法兰同心设置。
在一些实施例中，曲轴与法兰之间具有第一装配间隙，第一装配间隙的范围为0.005mm～0.05mm。
在一些实施例中，第一装配间隙的范围为0.01mm～0.03mm。
在一些实施例中，偏心部的偏心量等于曲轴与缸套的装配偏心量。
在一些实施例中，限位通道的两端贯通至交叉槽结构的外周面。
在一些实施例中，两个滑块分别与两个偏心部同心设置，滑块绕曲轴的轴心做圆周运动，通孔的孔壁与偏心部之间具有第一转动间隙，第一转动间隙的范围为0.005mm～0.05mm。
在一些实施例中，交叉槽结构与缸套同轴设置，交叉槽结构的外周面与缸套的内壁面之间具有第二转动间隙，第二转动间隙的尺寸范围为0.005mm～0.1mm。
在一些实施例中，第一夹角A的范围为160度-200度；第二夹角B的范围为80度-100度。
在一些实施例中，偏心部具有圆弧面，圆弧面与曲轴同轴设置，圆弧面的圆心角大于等于180度。
在一些实施例中，偏心部为圆柱形。
在一些实施例中，偏心部的近端与曲轴的轴体部分的外圆平齐；或，偏心部的近端突出于曲轴的轴体部分的外圆；或，偏心部的近端位于曲轴的轴体部分的外圆的内侧；其中，近端为偏心部的外侧面上与曲轴的轴线距离最小的位置。
在一些实施例中，两个偏心部在曲轴的轴向上间隔设置。
在一些实施例中，交叉槽结构具有中心孔，两个限位通道通过中心孔连通，中心孔的孔径大于曲轴的轴体部分的直径。
在一些实施例中，中心孔的孔径大于偏心部的直径。
在一些实施例中，限位通道具有与滑块滑动接触的一组相对设置的第一滑移面，滑块具有与第一滑移面配合的第二滑移面，滑块具有朝向限位通道的端部的挤压面，挤压面作为滑块的头部，两个第二滑移面通过挤压面连接，挤压面朝向变容积腔。
在一些实施例中，挤压面为弧面，弧面的弧心与通孔的中心之间的距离等于偏心 部的偏心量。
在一些实施例中，弧面的曲率半径与缸套的内圆的半径相等；或，弧面的曲率半径与缸套的内圆的半径具有差值，差值的范围为-0.05mm～0.025mm。
在一些实施例中，差值的范围为-0.02～0.02mm。
在一些实施例中，滑块在限位通道的截面上的形状与限位通道的截面的形状相适配。
在一些实施例中，滑块在滑块滑动方向上的投影呈方形，方形的宽度W与方形的高度H之间的比值范围满足：0.5～3。
在一些实施例中，方形的宽度W与方形的高度H之间的比值范围满足：1.5～2.5。
在一些实施例中，限位通道的截面为半圆形的一部分，滑块在滑块滑动方向上的投影包括弧线段和直线段，且弧形段的曲率半径的两倍为D1，直线段的长度为d1，D1与d1之间满足：d1/D1的比值范围为0.3～1。
在一些实施例中，D1与d1之间满足：d1/D1的比值范围为0.5～0.7。
在一些实施例中，缸套具有压缩进气口和压缩排气口，在任一滑块处于进气位置的情况下，压缩进气口与对应的变容积腔导通；在任一滑块处于排气位置的情况下，对应的变容积腔与压缩排气口导通。
在一些实施例中，挤压面在滑块滑动方向上的投影面积为S 滑块，缸套的压缩排气口的排气面积为S 排，S 滑块/S 排的比值范围为8～25。
在一些实施例中，S 滑块/S 排的比值范围为12～18。
在一些实施例中，缸套的内壁面具有吸气腔，吸气腔与压缩进气口连通。
在一些实施例中，吸气腔绕缸套的内壁面的周向延伸第一预设距离，以构成弧形吸气腔。
在一些实施例中，吸气腔为两个，两个吸气腔沿缸套的轴向间隔设置，缸套还具有吸气连通腔，两个吸气腔均与吸气连通腔连通，且压缩进气口通过吸气连通腔与吸气腔连通。
在一些实施例中，吸气连通腔沿缸套的轴向延伸第二预设距离，吸气连通腔的至少一端贯通缸套的轴向端面。
在一些实施例中，缸套的外壁上开设有排气腔，压缩排气口由缸套的内壁连通至排气腔处，流体机械还包括排气阀组件，排气阀组件设置在排气腔内并对应压缩排气口设置。
在一些实施例中，压缩排气口为两个，两个压缩排气口沿缸套的轴向间隔设置，排气阀组件为两组，两组排气阀组件分别对应两个压缩排气口设置。
在一些实施例中，缸套的轴向端面上还设置有连通孔，连通孔与排气腔连通，流体机械还包括法兰，法兰上设置有排气通道，连通孔与排气通道连通。
在一些实施例中，排气腔贯通至缸套的外壁面，流体机械还包括排气盖板，排气盖板与缸套连接并密封排气腔。
在一些实施例中，流体机械是压缩机。
在一些实施例中，缸套具有膨胀排气口和膨胀进气口，在任一滑块处于进气位置的情况下，膨胀排气口与对应的变容积腔导通；在任一滑块处于排气位置的情况下，对应的变容积腔与膨胀进气口导通。
在一些实施例中，缸套的内壁面具有膨胀排气腔，膨胀排气腔与膨胀排气口连通。
在一些实施例中，膨胀排气腔绕缸套的内壁面的周向延伸第一预设距离，以构成弧形膨胀排气腔，且膨胀排气腔由膨胀排气口处向膨胀进气口所在一侧延伸，膨胀排气腔的延伸方向与交叉槽结构的转动方向同向。
在一些实施例中，膨胀排气腔为两个，两个膨胀排气腔沿缸套的轴向间隔设置，缸套还具有膨胀排气连通腔，两个膨胀排气腔均与膨胀排气连通腔连通，且膨胀排气口通过膨胀排气连通腔与膨胀排气腔连通。
在一些实施例中，膨胀排气连通腔沿缸套的轴向延伸第二预设距离，膨胀排气连通腔的至少一端贯通缸套的轴向端面。
在一些实施例中，流体机械是膨胀机。
根据本公开的另一方面，提供了一种换热设备，包括上述实施例的流体机械。
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示出了根据本公开的一些实施例的压缩机运行的机构原理示意图；
图2示出了图1中的压缩机运行的机构原理示意图；
图3示出了根据本公开的实施例一的压缩机的内部结构示意图；
图4示出了图3中的压缩机的泵体组件的结构示意图；
图5示出了图4中的泵体组件的分解结构示意图；
图6示出了图5中的曲轴、交叉槽结构、滑块的装配结构示意图；
图7示出了图6中的曲轴、交叉槽结构、滑块的剖视结构示意图；
图8示出了图5中的交叉槽结构的结构示意图；
图9示出了图5中的滑块的结构示意图；
图10示出了图5中的曲轴的轴体部分和两个偏心部的结构示意图；
图11示出了图10中的曲轴的轴体部分和两个偏心部的偏心量的结构示意图；
图12示出了图4中的曲轴和缸套的装配偏心量的剖视结构示意图；
图13示出了图5中的缸套和下法兰处于分解状态时的结构示意图；
图14示出了图13中的缸套和下法兰之间的偏心量的结构示意图；
图15示出了图9中的滑块在通孔轴向上的结构示意图；
图16示出了图13中的缸套的结构示意图；
图17示出了图16中的缸套的另一视角的结构示意图；
图18示出了图17中的缸套剖视结构示意图；
图19示出了图17中的缸套的另一视角的剖视结构示意图；
图20示出了图19中的Y向视角的结构示意图；
图21示出了图12中的上法兰和缸套的另一个视角的剖视结构示意图，该图中，示出了泵体组件的排气路径；
图22示出了图4中的泵体组件的排气路径的剖视结构示意图；
图23示出了图5中的缸套和排气盖板处于分解状态时的结构示意图；
图24示出了图3中的压缩机处于吸气开始时的状态结构示意图；
图25示出了图3中的压缩机处于吸气过程中的状态结构示意图；
图26示出了图3中的压缩机处于吸气结束时的状态结构示意图；
图27示出了图3中的压缩机处于压缩气体时的状态结构示意图；
图28示出了图3中的压缩机处于排气过程中的状态结构示意图；
图29示出了图3中的压缩机处于排气结束时的状态结构示意图；
图30示出了图3中的具有轴承的泵体组件的剖视结构示意图，该图中，轴承位于轴向一端；
图31示出了图30中的交叉槽结构和轴承处于装配状态时的结构示意图；
图32示出了图3中的具有轴承的泵体组件的剖视结构示意图，该图中，轴承位于轴向两端；
图33示出了图32中的交叉槽结构和轴承处于装配状态时的结构示意图；
图34示出了图3中的具有轴承的泵体组件的剖视结构示意图，该图中，轴承位于轴向另一端；
图35示出了图34中的交叉槽结构和轴承处于装配状态时的结构示意图；
图36示出了图3中的具有轴承的泵体组件的剖视结构示意图，该图中，轴承位于周向外周侧；
图37示出了图36中的缸套、交叉槽结构和轴承处于装配状态时的结构示意图；
图38示出了图3中的具有轴承的泵体组件的剖视结构示意图，该图中，轴承位于两个子缸套之间；
图39示出了图38中的交叉槽结构和轴承处于装配状态时的结构示意图；
图40示出了图3中的交叉槽结构和滑块的横截面呈椭圆形的结构示意图；
图41示出了图3中的交叉槽结构和滑块的横截面呈方形的结构示意图；
图42示出了图3中的交叉槽结构和滑块的横截面呈梯形的结构示意图；
图43示出了图3中的交叉槽结构和滑块的横截面呈圆形的结构示意图；
图44示出了根据本公开的实施例二的压缩机的内部结构示意图；
图45示出了图44中的压缩机的泵体组件的结构示意图；
图46示出了图45中的泵体组件的交叉槽结构的结构示意图；
图47示出了根据本公开的实施例三的压缩机的内部结构示意图；
图48示出了图47中的压缩机的泵体组件的结构示意图；
图49示出了图47中的泵体组件的交叉槽结构的结构示意图；
图50示出了相关技术中的压缩机运行的机构原理示意图；
图51示出了相关技术中改进后的压缩机运行的机构原理示意图；
图52示出了图51中的压缩机运行的机构原理示意图，该图中，示出了驱动轴驱动滑块旋转的力臂；
图53示出了图51中的压缩机运行的机构原理示意图，该图中，限位槽结构的中心和偏心部的中心重合。
其中，上述附图包括以下附图标记：
10、曲轴；11、偏心部；12、轴体部分；
20、缸套；21、压缩进气口；22、压缩排气口；23、吸气腔；24、吸气连通腔；25、排气腔；26、连通孔；27、子缸套；
30、交叉槽结构；31、限位通道；311、变容积腔；32、中心孔；38、开孔；
40、滑块；41、通孔；42、挤压面；
50、法兰；51、排气通道；52、上法兰；53、下法兰；
60、排气阀组件；61、排气阀片；62、阀片挡板；
70、排气盖板；
80、分液器部件；81、壳体组件；82、电机组件；83、泵体组件；84、上盖组件；85、下盖组件；
90、紧固件；
200、轴承。
具体实施方式
下面将结合本公开实施例中的附图，对本公开实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅是本公开一部分实施例，而不是全部的实施例。以下对至少一个示例性实施例的描述实际上仅仅是说明性的，决不作为对本公开及其应用或使用的任何限制。基于本公开中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本公开保护的范围。
相关技术中，如图50所示，基于十字滑块机构提出了一种压缩机运行机构原理，即，以点O 1作为气缸中心、点O 2作为驱动轴中心、点O 3作为滑块中心，气缸与驱动轴偏心设置，其中，滑块中心O 3在直径为O 1O 2的圆上作圆周运动。
上述的运行机构原理中，气缸中心O 1和驱动轴中心O 2作为运动机构的两个旋转中心，同时，线段O 1O 2的中点O 0作为滑块中心O 3的虚拟中心，使得滑块相对于气缸作往复运动的同时，滑块还相对于驱动轴作往复运动。
由于线段O 1O 2的中点O 0为虚拟中心，无法设置平衡系统，导致压缩机高频振动特性恶化的问题，在上述运行机构原理的基础上，如图51所示，提出了一种以O 0作为驱动轴中心的运动机构，即，气缸中心O 1和驱动轴中心O 0作为运动机构的两个旋转中心，驱动轴具有偏心部，滑块与偏心部同轴设置，驱动轴与气缸的装配偏心量等于偏心部的偏心量，使得滑块中心O 3以驱动轴中心O 0为圆心并以O 1O 0为半径做圆周运动。
对应的提出了一套运行机构，包括气缸、限位槽结构、滑块和驱动轴，其中，限位槽结构可转动地设置在气缸内，且气缸与限位槽结构同轴设置，即，气缸中心O 1 也是限位槽结构的中心，滑块相对于限位槽结构往复运动，滑块与驱动轴的偏心部同轴装配，滑块绕驱动轴的轴体部分做圆周运动，具体地运动过程为：驱动轴转动，带动滑块绕驱动轴的轴体部分的中心公转，滑块同时相对于偏心部自转，且滑块在限位槽结构的限位槽内往复运动，并推动限位槽结构旋转。
但是，如图52所示，驱动轴驱动滑块旋转的力臂L的长度为L＝2e×cosθ×cosθ，其中，e为偏心部的偏心量，θ为O 1O 0连线与滑块在限位槽内滑动方向之间的夹角。
如图53所示，当气缸中心O 1(即，限位槽结构的中心)和偏心部的中心重合时，驱动轴的驱动力的合力经过限位槽结构的中心，即，施加在限位槽结构上的转矩为零，限位槽结构无法转动，此时的运动机构处于死点位置，无法驱动滑块旋转。
基于此，本公开提出了一种具备两个限位通道的交叉槽结构和双滑块的机构原理，并基于该原理构建了一种流体机械例如压缩机和膨胀机，该流体机械具备能效高、噪音小的特点，下面以压缩机为例，具体介绍基于具备两个限位通道的交叉槽结构和双滑块的压缩机。
为了改善了现有技术中的压缩机的能效较低、噪音较大的问题，本公开提供了一种流体机械和换热设备，其中，换热设备包括下述的流体机械。
应用本公开的技术方案，通过将交叉槽结构设置成具有两个限位通道的结构形式，并对应设置两个滑块，曲轴的两个偏心部对应伸入两个滑块的两个通孔内，同时，两个滑块对应滑动设置在两个限位通道内并形成变容积腔，由于两个偏心部之间的第一夹角A为两个限位通道的延伸方向之间的第二夹角B的二倍，这样，当两个滑块中的一个处于死点位置时，即，与处于死点位置处的滑块对应的偏心部的驱动转矩为0，处于死点位置处的滑块无法继续旋转，而此时两个偏心部中的另一个偏心部驱动对应的滑块的驱动转矩为最大值，确保具有最大驱动转矩的偏心部能够正常驱动对应的滑块旋转，从而通过该滑块来带动交叉槽结构转动，进而通过交叉槽结构带动处于死点位置处的滑块继续旋转，实现了流体机械的稳定运行，避开了运动机构的死点位置，提升了流体机械的运动可靠性，从而确保换热设备的工作可靠性。
此外，通过将两个法兰分别设置在缸套的轴向两端，同时，曲轴穿过两个法兰和缸套，确保两个法兰能够对缸套起到限位作用，从而确保缸套的安装可靠性。
在一些实施例中，由于本公开提供的流体机械能够稳定运行，即，确保了流体机械例如压缩机和膨胀机的能效较高、噪音较小，从而确保换热设备的工作可靠性。
在一些实施例中，本公开中的流体机械包括两个法兰50、曲轴10、缸套20、交叉槽结构30和两个滑块40，其中，曲轴10沿其轴向设置有两个偏心部11，两个偏心部11之间具有第一夹角A的相位差；曲轴10与缸套20偏心设置且偏心距离固定；交叉槽结构30可转动地设置在缸套20内，交叉槽结构30具有两个限位通道31，两个限位通道31沿曲轴10的轴向顺次设置，限位通道31的延伸方向垂直于曲轴10的轴向，且两个限位通道31的延伸方向之间具有第二夹角B的相位差，其中，第一夹角A为第二夹角B的二倍；滑块40具有通孔41，滑块40为两个，曲轴10穿过两个法兰50和缸套20，且两个偏心部11对应伸入两个滑块40的两个通孔41内，两个滑块40对应滑动设置在两个限位通道31内并形成变容积腔311，变容积腔311位于滑块40的滑动方向上，曲轴10被配置为通过转动以带动滑块40在限位通道31内往复滑动的同时与交叉槽结构30相互作用，使得交叉槽结构30、滑块40在缸套20内转动。
通过将交叉槽结构30设置成具有两个限位通道31的结构形式，并对应设置两个滑块40，曲轴的两个偏心部11对应伸入两个滑块40的两个通孔41内，同时，两个滑块40对应滑动设置在两个限位通道31内并形成变容积腔311，由于两个偏心部11之间的第一夹角A为两个限位通道31的延伸方向之间的第二夹角B的二倍，这样，当两个滑块40中的一个处于死点位置时，即，与处于死点位置处的滑块40对应的偏心部11的驱动转矩为0，处于死点位置处的滑块40无法继续旋转，而此时两个偏心部11中的另一个偏心部11驱动对应的滑块40的驱动转矩为最大值，确保具有最大驱动转矩的偏心部11能够正常驱动对应的滑块40旋转，从而通过该滑块40来带动交叉槽结构30转动，进而通过交叉槽结构30带动处于死点位置处的滑块40继续旋转，实现了流体机械的稳定运行，避开了运动机构的死点位置，提升了流体机械的运动可靠性，从而确保换热设备的工作可靠性。
此外，通过将两个法兰50分别设置在缸套20的轴向两端，同时，曲轴10穿过两个法兰50和缸套20，确保两个法兰50能够对缸套20起到限位作用，从而确保缸套20的安装可靠性。
在一些实施例中，由于本公开提供的流体机械能够稳定运行，即，确保了流体机械例如压缩机和膨胀机的能效较高、噪音较小，从而确保换热设备的工作可靠性。
需要说明的是，在本公开中，第一夹角A和第二夹角B均不为零。
如图1和图2所示，当上述的流体机械运行时，曲轴10绕曲轴10的轴心O 0自 转；交叉槽结构30绕曲轴10的轴心O 0公转，曲轴10的轴心O 0与交叉槽结构30的轴心O 1偏心设置且偏心距离固定；第一个滑块40以曲轴10的轴心O 0为圆心做圆周运动，且第一个滑块40的中心O 3与曲轴10的轴心O 0之间的距离等于曲轴10对应的第一个偏心部11的偏心量，且偏心量等于曲轴10的轴心O 0与交叉槽结构30的轴心O 1之间的偏心距离，曲轴10转动以带动第一个滑块40做圆周运动，且第一个滑块40与交叉槽结构30相互作用并在交叉槽结构30的限位通道31内往复滑动；第二个滑块40以曲轴10的轴心O 0为圆心做圆周运动，且第二个滑块40的中心O 4与曲轴10的轴心O 0之间的距离等于曲轴10对应的第二个偏心部11的偏心量，且偏心量等于曲轴10的轴心O 0与交叉槽结构30的轴心O 1之间的偏心距离，曲轴10转动以带动第二个滑块40做圆周运动，且第二个滑块40与交叉槽结构30相互作用并在交叉槽结构30的限位通道31内往复滑动。
如上述方法运行的流体机械，构成了十字滑块机构，该运行方法采用十字滑块机构原理，其中，曲轴10的两个偏心部11分别作为第一连杆L 1和第二连杆L 2，交叉槽结构30的两个限位通道31分别作为第三连杆L 3和第四连杆L 4，且第一连杆L 1和第二连杆L 2的长度相等(请参考图1)。
如图1所示，第一连杆L 1和第二连杆L 2之间具有第一夹角A，第三连杆L 3和第四连杆L 4之间具有第二夹角B，其中，第一夹角A为第二夹角B的二倍。
如图2所示，曲轴10的轴心O 0与交叉槽结构30的轴心O 1之间的连线为连线O 0O 1，第一连杆L 1与连线O 0O 1之间具有第三夹角C，对应的第三连杆L 3与连线O 0O 1之间具有第四夹角D，其中，第三夹角C为第四夹角D的二倍；第二连杆L 2与连线O 0O 1之间具有第五夹角E，对应的第四连杆L 4与连线O 0O 1之间具有第六夹角F，其中，第五夹角E为第六夹角F的二倍；第三夹角C与第五夹角E之和是第一夹角A，第四夹角D和第六夹角F之和是第二夹角B。
在一些实施例中，运行方法还包括滑块40相对于偏心部11的自转角速度与滑块40绕曲轴10的轴心O 0的公转角速度相同；交叉槽结构30绕曲轴10的轴心O 0的公转角速度与滑块40相对于偏心部11的自转角速度相同。
具体而言，曲轴10的轴心O 0相当于第一连杆L 1和第二连杆L 2的旋转中心，交叉槽结构30的轴心O 1相当于第三连杆L 3和第四连杆L 4的旋转中心；曲轴10的两个偏心部11分别作为第一连杆L 1和第二连杆L 2，交叉槽结构30的两个限位通道31分别作为第三连杆L 3和第四连杆L 4，且第一连杆L 1和第二连杆L 2的长度相等，这样， 曲轴10转动的同时，曲轴10上的偏心部11带动对应的滑块40绕曲轴10的轴心O 0公转，同时滑块40相对于偏心部11能够自转，且二者的相对转动速度相同，由于第一个滑块40和第二个滑块40分别在两个对应的限位通道31内往复运动，并带动交叉槽结构30做圆周运动，受交叉槽结构30的两个限位通道31的限位，两个滑块40的运动方向始终具有第二夹角B的相位差，当两个滑块40中的一个处于死点位置时，用于驱动两个滑块40中的另一个的偏心部11具有最大的驱动转矩，具有最大驱动转矩的偏心部11能够正常驱动对应的滑块40旋转，从而通过该滑块40来带动交叉槽结构30转动，进而通过交叉槽结构30带动处于死点位置处的滑块40继续旋转，实现了流体机械的稳定运行，避开了运动机构的死点位置，提升了流体机械的运动可靠性，从而确保换热设备的工作可靠性。
需要说明的是，在本公开中，偏心部11的驱动转矩的最大力臂为2e。
在该运动方法下，滑块40的运行轨迹为圆，且该圆以曲轴10的轴心O 0为圆心以连线O 0O 1为半径。
需要说明的是，在本公开中，在曲轴10转动的过程中，曲轴10转动2圈，完成4次吸排气过程。
下面将给出三个可选的实施方式，以对流体机械的结构进行详细的介绍，以便能够通过结构特征更好地阐述流体机械的运行方法。
实施例一
如图3至图43所示，交叉槽结构30的两端的端面上均预留有供曲轴10伸出的开孔38，开孔38与交叉槽结构30同心设置，开孔38与限位通道31连通。这样，确保曲轴10能够顺利穿过交叉槽结构30的同时，当交叉槽结构30位于缸套20内时，能够对缸套20进行良好的封闭。
如图3至图43所示，流体机械还包括法兰50，法兰50设置在缸套20的轴向的端部，曲轴10与法兰50同心设置，交叉槽结构30与缸套20同轴设置，曲轴10与交叉槽结构30的装配偏心量由法兰50和缸套20相对位置关系确定，其中，法兰50通过紧固件90固定在缸套20上，法兰50的轴心与缸套20内圈的轴心的相对位置通过法兰50调心控制，法兰50的轴心与缸套20内圈的轴心的相对位置决定了曲轴10的轴心和交叉槽结构30的轴心的相对位置，通过法兰50调心的本质就是使得偏心部11的偏心量等于曲轴10与缸套20的装配偏心量。
具体地，如图11所示，两个偏心部11的偏心量均等于e，如图12所示，曲轴 10和缸套20之间的装配偏心量为e(由于交叉槽结构30与缸套20同轴设置，曲轴10和交叉槽结构30之间的装配偏心量即曲轴10和缸套20之间的装配偏心量)，法兰50包括上法兰52和下法兰53，如图14所示，缸套20的内圈轴心与下法兰53的内圈轴心之间的距离为e，即，等于偏心部11的偏心量。
在一些实施例中，曲轴10与法兰50之间具有第一装配间隙，第一装配间隙的范围为0.005mm～0.05mm。
在一些实施例中，第一装配间隙的范围为0.01mm～0.03mm。
如图5和图8所示，限位通道31的两端贯通至交叉槽结构30的外周面。这样，有利于降低交叉槽结构30的加工制造难度。
在一些实施例中，两个滑块40分别与两个偏心部11同心设置，滑块40绕曲轴10的轴心做圆周运动，通孔41的孔壁与偏心部11之间具有第一转动间隙，第一转动间隙的范围为0.005mm～0.05mm。
在一些实施例中，交叉槽结构30与缸套20同轴设置，交叉槽结构30的外周面与缸套20的内壁面之间具有第二转动间隙，第二转动间隙的尺寸0.005mm～0.1mm。
如图4至图7、图10至图12所示，曲轴10的轴体部分12一体成型，且轴体部分12仅具有一个轴心。这样，便于轴体部分12的一次成型，从而降低了轴体部分12的加工制造难度。
需要说明的是，在本公开一个未图示的实施例中，曲轴10的轴体部分12包括沿其轴向连接的第一段和第二段，第一段与第二段同轴设置，两个偏心部11分别设置在第一段和第二段上。
在一些实施例中，第一段与第二段可拆卸地连接。这样，确保曲轴10的装配和拆卸的便捷性。
如图4至图7、图10至图12所示，曲轴10的轴体部分12与偏心部11一体成型。这样，便于曲轴10的一次成型，从而降低了曲轴10的加工制造难度。
需要说明的是，在本公开一个未图示的实施例中，曲轴10的轴体部分12与偏心部11可拆卸地连接。这样，便于偏心部11的安装和拆卸。
需要说明的是，在本公开中，第一夹角A的范围为160度-200度；第二夹角B的范围为80度-100度。这样，只要满足第一夹角A是第二夹角B的二倍的关系即可。
在一些实施例中，第一夹角A为160度，第二夹角B为80度。
在一些实施例中，第一夹角A为165度，第二夹角B为82.5度。
在一些实施例中，第一夹角A为170度，第二夹角B为85度。
在一些实施例中，第一夹角A为175度，第二夹角B为87.5度。
在一些实施例中，第一夹角A为180度，第二夹角B为90度。
在一些实施例中，第一夹角A为185度，第二夹角B为92.5度。
在一些实施例中，第一夹角A为190度，第二夹角B为95度。
在一些实施例中，第一夹角A为195度，第二夹角B为97.5度。
需要说明的是，在本公开中，偏心部11具有圆弧面，圆弧面与曲轴10同轴设置，圆弧面的圆心角大于等于180度。这样，确保偏心部11的圆弧面能够对滑块40施加有效驱动力的作用，从而确保滑块40的运动可靠性。
如图4至图7、图10至图12所示，偏心部11为圆柱形。
在一些实施例中，偏心部11的近端与曲轴10的轴体部分的外圆平齐。
在一些实施例中，偏心部11的近端突出于曲轴10的轴体部分的外圆。
在一些实施例中，偏心部11的近端位于曲轴10的轴体部分的外圆的内侧。
在上述实施例中，近端为偏心部11的外侧面上与曲轴10的轴线距离最小的位置。
需要说明的是，在本公开一个未图示的实施例中，滑块40包括多个子滑块，多个子滑块拼接后围成通孔41。
如图4至图7、图10至图12所示，两个偏心部11在曲轴10的轴向上间隔设置。这样，在装配曲轴10、缸套20和两个滑块40的过程中，确保两个偏心部11之间的间隔距离能够为缸套20提供装配空间，以确保装配便捷性。
如图5所示，交叉槽结构30具有中心孔32，两个限位通道31通过中心孔32连通，中心孔32的孔径大于曲轴10的轴体部分的直径。这样，确保曲轴10能够顺利地穿过中心孔32。
在一些实施例中，中心孔32的孔径大于偏心部11的直径。这样，确保曲轴10的偏心部11能够顺利地穿过中心孔32。
如图8、图9和图15所示，滑块40在通孔41的轴向的投影具有两条相对平行的直线段以及连接两条直线段的端部的弧线段。限位通道31具有与滑块40滑动接触的一组相对设置的第一滑移面S1，滑块40具有与第一滑移面S1配合的第二滑移面S2，滑块40具有朝向限位通道31的端部的挤压面42，挤压面42作为滑块40的头部，两个第二滑移面S2通过挤压面42连接，挤压面42朝向变容积腔311。这样，滑块40的第二滑移面S2在其通孔41的轴向的投影为直线段，同时，滑块40的挤压面42 在其通孔41的轴向的投影为弧线段。
具体地，挤压面42为弧面，弧面的弧心与通孔41的中心之间的距离等于偏心部11的偏心量。图15中，滑块40的通孔41中心为O滑块，两个弧面的弧心与通孔41的中心之间的距离均为e，即，偏心部11的偏心量，图12中的X虚线表示两个弧面的弧心所在的圆。
在一些实施例中，弧面的曲率半径与缸套20的内圆的半径相等。
在一些实施例中，弧面的曲率半径与缸套20的内圆的半径具有差值，差值的范围为-0.05mm～0.025mm。
在一些实施例中，差值的范围为-0.02～0.02mm。
如图8和图9所示，滑块40在限位通道31的截面上的形状与限位通道31的截面的形状相适配。这样，确保滑块40在限位通道31内的滑动平稳性。
在一些实施例中，限位通道31的截面为半圆形、圆形、长方形、椭圆形、正方形和梯形中的一种。
在一些实施例中，滑块40在滑块40滑动方向上的投影呈方形，方形的宽度W与方形的高度H之间的比值范围满足：0.5～3。
在一些实施例中，方形的宽度W与方形的高度H之间的比值范围满足：1.5～2.5。
在一些实施例中，限位通道31的截面为半圆形的一部分，滑块40在滑块40滑动方向上的投影由一段弧线段与直线段构成，且弧形段的曲率半径的两倍为D1，直线段的长度为d1，D1与d1之间满足：d1/D1的比值范围为0.3～1。
在一些实施例中，D1与d1之间满足：d1/D1的比值范围为0.5～0.7。
在一些实施例中，挤压面42在滑块40滑动方向上的投影面积为S 滑块，缸套20的压缩排气口22的排气面积为S 排，S 滑块/S 排的比值范围为8～25。
在一些实施例中，S 滑块/S 排的比值范围为12～18。
需要说明的是，本实施例示出的流体机械为压缩机，如图3所示，压缩机包括分液器部件80、壳体组件81、电机组件82、泵体组件83、上盖组件84和下盖组件85，其中，分液器部件80设置在壳体组件81的外部，上盖组件84装配在壳体组件81的上端，下盖组件85装配在壳体组件81的下端，电机组件82和泵体组件83均位于壳体组件81的内部，其中，电机组件82位于泵体组件83的上方，或者，电机组件82位于泵体组件83的下方。压缩机的泵体组件83包括上述的曲轴10、缸套20、交叉槽结构30、滑块40、上法兰52和下法兰53。
在一些实施例中，上述各部件通过焊接、热套、或冷压的方式连接。
整个泵体组件83的装配过程如下：下法兰53固定在缸套20上，两个滑块40分别置于对应的两个限位通道31内，曲轴10的两个偏心部11分别伸入对应的两个滑块40的两个通孔41内，再将组装好的曲轴10、交叉槽结构30和两个滑块40置于缸套20内，曲轴10的一端安装在下法兰53上，曲轴10的另一端穿过上法兰52设置，具体可参见图4和图5。
需要说明的是，在本实施例中，滑块40、限位通道31、缸套20和上法兰52(或下法兰53)围成的封闭空间即为变容积腔311，泵体组件83共具有4个变容积腔311，在曲轴10转动的过程中，曲轴10转动2圈，单个变容积腔311完成1次吸排气过程，对压缩机而言，曲轴10转动2圈，共计完成4次吸排气过程。
如图24至图29所示，滑块40在限位通道31内往复运动的过程中，同时相对于缸套20旋转，图24至图26中，滑块40顺时针从0度向180度转动的过程中，变容积腔311增大，在变容积腔311增大的过程中，变容积腔311与缸套20的吸气腔23连通，滑块40转动至180度时，变容积腔311的容积达到最大值，此时的变容积腔311与吸气腔23脱离，由此完成吸气作业，图27至图29中，滑块40继续沿顺时针方向从180度向360度转动的过程中，变容积腔311减小，滑块40对变容积腔311内的气体进行压缩，当滑块40转动至该变容积腔311与压缩排气口22连通，且当变容积腔311内的气体达到排气压力时，排气阀组件60的排气阀片61开启，开始排气作业，直至压缩结束后进入下一个周期。
如图24至图29所示，以M标记的点作为滑块40与曲轴10相对运动的参考点，图25表示滑块40顺时针从0度向180度转动的过程，滑块40转动的角度为θ1，对应的曲轴10转动的角度为2θ1，图27中表示滑块40继续沿顺时针方向从180度向360度转动的过程，滑块40转动的角度为180°+θ2，对应的曲轴10转动的角度为360°+2θ2，图28中表示滑块40继续沿顺时针方向从180度向360度转动的过程，且变容积腔311与压缩排气口22连通，滑块40转动的角度为180°+θ3，对应的曲轴10转动的角度为360°+2θ3，即，滑块40转1圈，对应的曲轴10转2圈，其中，θ1＜θ2＜θ3。
具体而言，如图13、图16至图29所示，缸套20具有压缩进气口21和压缩排气口22，当任一滑块40处于进气位置时，压缩进气口21与对应的变容积腔311导通；当任一滑块40处于排气位置时，对应的变容积腔311与压缩排气口22导通。
如图13、图16至图29所示，缸套20的内壁面具有吸气腔23，吸气腔23与压缩进气口21连通。这样，确保吸气腔23能够蓄存有大量的气体，以使的变容积腔311能够饱满吸气，从而使得压缩机能够足量吸气，并在吸气不足时，能够及时供给蓄存气体给变容积腔311，以保证压缩机的压缩效率。
在一些实施例中，吸气腔23为在缸套20的内壁面沿径向挖空形成的腔体，吸气腔23可以是1个，也可以是上下2个。
具体而言，吸气腔23绕缸套20的内壁面的周向延伸第一预设距离，以构成弧形吸气腔23。这样，确保吸气腔23的容积足够大，以蓄存大量的气体。
如图13、图16、图18和图23所示，吸气腔23为两个，两个吸气腔23沿缸套20的轴向间隔设置，缸套20还具有吸气连通腔24，两个吸气腔23均与吸气连通腔24连通，且压缩进气口21通过吸气连通腔24与吸气腔23连通。这样，有利于增大吸气腔23的容积，从而减小吸气压力脉动。
如图13、图16、图18和图23所示，吸气连通腔24沿缸套20的轴向延伸第二预设距离，吸气连通腔24的至少一端贯通缸套20的轴向端面。这样，便于从缸套20的端面上开设吸气连通腔24，确保吸气连通腔24的加工便捷性。
如图13、图16至图29所示，缸套20的外壁上开设有排气腔25，压缩排气口22由缸套20的内壁连通至排气腔25处，流体机械还包括排气阀组件60，排气阀组件60设置在排气腔25内并对应压缩排气口22设置。这样，排气腔25用于容纳排气阀组件60，有效减少了排气阀组件60的占用空间，使得部件合理布置，提高了缸套20的空间利用率。
如图20至图22所示，压缩排气口22为两个，两个压缩排气口22沿缸套20的轴向间隔设置，排气阀组件60为两组，两组排气阀组件60分别对应两个压缩排气口22设置。这样，由于两个压缩排气口22分别设置有两组排气阀组件60，有效避免变容积腔311内的气体大量泄漏，保证了变容积腔311的压缩效率。
如图19所示，排气阀组件60通过紧固件90与缸套20连接，排气阀组件60包括排气阀片61和阀片挡板62，排气阀片61设置在排气腔25内并遮挡对应的压缩排气口22，阀片挡板62重叠设置在排气阀片61上。这样，阀片挡板62的设置，有效避免了排气阀片61过渡开启，从而保证了缸套20的排气性能。
在一些实施例中，紧固件90为螺钉。
如图13、图16、图21和图22所示，缸套20的轴向端面上还设置有连通孔26， 连通孔26与排气腔25连通，流体机械还包括法兰50，法兰50上设置有排气通道51，连通孔26与排气通道51连通。这样，确保缸套20的排气可靠性。
如图23所示，排气腔25贯通至缸套20的外壁面，流体机械还包括排气盖板70，排气盖板70与缸套20连接并密封排气腔25。这样，排气盖板70起到将变容积腔311与泵体组件83的外部空间隔开的作用。
具体地，当变容积腔311与压缩排气口22连通后，变容积腔311的压力达到排气压力时，排气阀片61打开，压缩的气体经过压缩排气口22进入排气腔25内，并经过缸套20上的连通孔26，再经排气通道51排出并进入泵体组件83的外部空间(即压缩机的腔体)，由此完成排气过程。
在一些实施例中，排气盖板70通过紧固件90固定在缸套20上。
在一些实施例中，紧固件90为螺钉。
在一些实施例中，排气盖板70的外轮廓与排气腔25的外轮廓相适配。
下面对压缩机的运行进行具体介绍：
如图3所示，电机组件82带动曲轴10转动，曲轴10的两个偏心部11分别驱动对应的两个滑块40运动，滑块40绕曲轴10的轴心做公转的同时，滑块40相对于偏心部11自转，且滑块40沿限位通道31往复运动，并带动交叉槽结构30在缸套20内转动，滑块40公转的同时沿限位通道31进行往复运动而构成十字滑块机构运动方式。
其他使用场合：该压缩机将吸、排气口交换位置，可以作为膨胀机使用。即，将压缩机的排气口作为膨胀机吸气口，通入高压气体，其他推动机构转动，膨胀后通过压缩机吸气口(膨胀机排气口)排出气体。
当流体机械为膨胀机时，缸套20具有膨胀排气口和膨胀进气口，当任一滑块40处于进气位置时，膨胀排气口与对应的变容积腔311导通；当任一滑块40处于排气位置时，对应的变容积腔311与膨胀进气口导通。
在一些实施例中，缸套20的内壁面具有膨胀排气腔，膨胀排气腔与膨胀排气口连通。
在一些实施例中，膨胀排气腔绕缸套20的内壁面的周向延伸第一预设距离，以构成弧形膨胀排气腔，且膨胀排气腔由膨胀排气口处向膨胀进气口所在一侧延伸，膨胀排气腔的延伸方向与交叉槽结构30的转动方向同向。
在一些实施例中，膨胀排气腔为两个，两个膨胀排气腔沿缸套20的轴向间隔设 置，缸套20还具有膨胀排气连通腔，两个膨胀排气腔均与膨胀排气连通腔连通，且膨胀排气口通过膨胀排气连通腔与膨胀排气腔连通。
在一些实施例中，膨胀排气连通腔沿缸套20的轴向延伸第二预设距离，膨胀排气连通腔的至少一端贯通缸套20的轴向端面。
如图30和31所示，交叉槽结构30的轴向一端套设有轴承200，并位于交叉槽结构30的轴向一端的上方侧。
如图32和图33所示，交叉槽结构30的轴向两端均套设有轴承200。
如图34和图35所示，交叉槽结构30的轴向另一端套设有轴承200，并位于交叉槽结构30的轴向一端的下方侧。
如图36和图37所示，轴承200设置在缸套20内且轴承200的外圈与缸套20的内壁贴合，同时限定轴承200的高度H1与缸套20的高度H2之间的比值大于0.9且小于1。
如图38和39所示，缸套20包括两个子缸套27，轴承200设置在两个子缸套27之间，且轴承200的轴向两端的端面分别与两个子缸套27朝向轴承200一侧的端面贴合，轴承200与两个子缸套27同心设置。
如图40至图43所示，限位通道31的截面为半圆形、圆形、长方形、椭圆形、正方形和梯形中的一种。
实施例二
如图44至图46所示，交叉槽结构30至少一端的端面呈敞口状，且呈敞口状一侧的限位通道31沿交叉槽结构30的轴向直接贯通至端面，交叉槽结构30没有呈敞口状的一端的端面预留有供曲轴10伸出的开孔38，交叉槽结构30没有呈敞口状的一端即为远离呈敞口状的一端，开孔38与交叉槽结构30同心设置，开孔38与限位通道31连通。
需要说明的是，在本实施例中，交叉槽结构30的一端呈敞口状，且呈敞口状的一端位于上方。
实施例三
如图47至图49所示，本实施例与实施例三的区别在于，交叉槽结构30的一端呈敞口状，且呈敞口状的一端位于下方。
上述实施例一、实施例二和实施例三中描述一些技术方案在不造成冲突的情况下可相互借鉴。
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、操作、器件、组件和/或它们的组合。
除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、数字表达式和数值不限制本公开的范围。同时，应当明白，为了便于描述，附图中所示出的各个部分的尺寸并不是按照实际的比例关系绘制的。对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，所述技术、方法和设备应当被视为授权说明书的一部分。在这里示出和讨论的所有示例中，任何具体值应被解释为仅仅是示例性的，而不是作为限制。因此，示例性实施例的其它示例可以具有不同的值。应注意到：相似的标号和字母在下面的附图中表示类似项，因此，一旦某一项在一个附图中被定义，则在随后的附图中不需要对其进行进一步讨论。
为了便于描述，在这里可以使用空间相对术语，如“在……之上”、“在……上方”、“在……上表面”、“上面的”等，用来描述如在图中所示的一个器件或特征与其他器件或特征的空间位置关系。应当理解的是，空间相对术语旨在包含除了器件在图中所描述的方位之外的在使用或操作中的不同方位。例如，如果附图中的器件被倒置，则描述为“在其他器件或构造上方”或“在其他器件或构造之上”的器件之后将被定位为“在其他器件或构造下方”或“在其他器件或构造之下”。因而，示例性术语“在……上方”可以包括“在……上方”和“在……下方”两种方位。该器件也可以其他不同方式定位(旋转90度或处于其他方位)，并且对这里所使用的空间相对描述作出相应解释。
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。
以上所述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 (45)

  1. 一种流体机械，包括：
    两个法兰(50)；
    曲轴(10)，所述曲轴(10)沿其轴向设置有两个偏心部(11)，两个所述偏心部(11)之间具有第一夹角A的相位差；
    缸套(20)，所述曲轴(10)与所述缸套(20)偏心设置且偏心距离固定；
    交叉槽结构(30)，所述交叉槽结构(30)可转动地设置在所述缸套(20)内，所述交叉槽结构(30)具有两个限位通道(31)，两个所述限位通道(31)沿所述曲轴(10)的轴向顺次设置，所述限位通道(31)的延伸方向垂直于所述曲轴(10)的轴向，且两个所述限位通道(31)的延伸方向之间具有第二夹角B的相位差，其中，所述第一夹角A为所述第二夹角B的二倍；和
    两个滑块(40)，所述滑块(40)具有通孔(41)；
    其中，所述曲轴(10)穿过两个所述法兰(50)和所述缸套(20)，且两个所述偏心部(11)对应伸入两个所述滑块(40)的两个所述通孔(41)内，两个所述滑块(40)对应滑动设置在两个所述限位通道(31)内并形成变容积腔(311)，所述变容积腔(311)位于滑块(40)的滑动方向上，所述曲轴(10)被配置为通过转动带动所述滑块(40)在所述限位通道(31)内往复滑动，同时与所述交叉槽结构(30)相互作用，使得所述交叉槽结构(30)、所述滑块(40)在所述缸套(20)内转动。
  2. 根据权利要求1所述的流体机械，其中所述交叉槽结构(30)至少一端的端面呈敞口状，且呈敞口状一侧的所述限位通道(31)沿所述交叉槽结构(30)的轴向直接贯通至所述端面，所述交叉槽结构(30)远离呈敞口状的一端的端面预留有供所述曲轴(10)伸出的开孔(38)，所述开孔(38)与所述交叉槽结构(30)同心设置，所述开孔(38)与所述限位通道(31)连通。
  3. 根据权利要求1或2所述的流体机械，其中所述交叉槽结构(30)的两端的端面上均预留有供所述曲轴(10)伸出的开孔(38)，所述开孔(38)与所述交叉槽结构(30)同心设置，所述开孔(38)与所述限位通道(31)连通。
  4. 根据权利要求1～3任一项所述的流体机械，其中所述曲轴(10)与所述法兰(50)同心设置。
  5. 根据权利要求1～4任一项所述的流体机械，其中所述曲轴(10)与所述法兰(50) 之间具有第一装配间隙，所述第一装配间隙的范围为0.005mm～0.05mm。
  6. 根据权利要求5所述的流体机械，其中所述第一装配间隙的范围为0.01mm～0.03mm。
  7. 根据权利要求1～6任一项所述的流体机械，其中所述偏心部(11)的偏心量等于所述曲轴(10)与所述缸套(20)的装配偏心量。
  8. 根据权利要求1～7任一项所述的流体机械，其中所述限位通道(31)的两端贯通至所述交叉槽结构(30)的外周面。
  9. 根据权利要求1～8任一项所述的流体机械，其中两个所述滑块(40)分别与两个所述偏心部(11)同心设置，所述滑块(40)绕所述曲轴(10)的轴心做圆周运动，所述通孔(41)的孔壁与所述偏心部(11)之间具有第一转动间隙，所述第一转动间隙的范围为0.005mm～0.05mm。
  10. 根据权利要求1～9任一项所述的流体机械，其中所述交叉槽结构(30)与所述缸套(20)同轴设置，所述交叉槽结构(30)的外周面与所述缸套(20)的内壁面之间具有第二转动间隙，所述第二转动间隙的范围为0.005mm～0.1mm。
  11. 根据权利要求1～10任一项所述的流体机械，其中所述第一夹角A的范围为160度-200度；所述第二夹角B的范围为80度-100度。
  12. 根据权利要求1～11任一项所述的流体机械，其中所述偏心部(11)具有圆弧面，所述圆弧面与所述曲轴(10)同轴设置，所述圆弧面的圆心角大于等于180度。
  13. 根据权利要求1～12任一项所述的流体机械，其中所述偏心部(11)为圆柱形。
  14. 根据权利要求13所述的流体机械，其中所述偏心部(11)的近端被布置成以下之一，其中所述近端为所述偏心部(11)的外侧面上与所述曲轴(10)的轴线距离最小的位置：
    所述偏心部(11)的近端与所述曲轴(10)的轴体部分的外圆平齐；
    所述偏心部(11)的近端突出于所述曲轴(10)的轴体部分的外圆；
    所述偏心部(11)的近端位于所述曲轴(10)的轴体部分的外圆的内侧。
  15. 根据权利要求1～14任一项所述的流体机械，其中两个所述偏心部(11)在所述曲轴(10)的轴向上间隔设置。
  16. 根据权利要求1～15任一项所述的流体机械，其中所述交叉槽结构(30)具有中心孔(32)，两个所述限位通道(31)通过所述中心孔(32)连通，所述中心孔 (32)的孔径大于所述曲轴(10)的轴体部分的直径。
  17. 根据权利要求16所述的流体机械，其中所述中心孔(32)的孔径大于所述偏心部(11)的直径。
  18. 根据权利要求1～17任一项所述的流体机械，其中所述限位通道(31)具有与所述滑块(40)滑动接触的一组相对设置的第一滑移面(S1)，所述滑块(40)具有与所述第一滑移面(S1)配合的第二滑移面(S2)，所述滑块(40)具有朝向所述限位通道(31)的端部的挤压面(42)，所述挤压面(42)作为所述滑块(40)的头部，两个所述第二滑移面(S2)通过所述挤压面(42)连接，所述挤压面(42)朝向所述变容积腔(311)。
  19. 根据权利要求18所述的流体机械，其中所述挤压面(42)为弧面，所述弧面的弧心与所述通孔(41)的中心之间的距离等于所述偏心部(11)的偏心量。
  20. 根据权利要求19所述的流体机械，其中，
    所述弧面的曲率半径与缸套(20)的内圆的半径相等；或，
    所述弧面的曲率半径与缸套(20)的内圆的半径具有差值，所述差值的范围为-0.05mm～0.025mm。
  21. 根据权利要求20所述的流体机械，其中所述差值的范围为-0.02～0.02mm。
  22. 根据权利要求1～21任一项所述的流体机械，其特征在于，所述滑块(40)在所述限位通道(31)的截面上的形状与所述限位通道(31)的截面的形状相适配。
  23. 根据权利要求1～22任一项所述的流体机械，其中所述滑块(40)在所述滑块(40)滑动方向上的投影呈方形，所述方形的宽度W与所述方形的高度H之间的比值的范围满足：0.5～3。
  24. 根据权利要求23所述的流体机械，其中所述方形的宽度W与所述方形的高度H之间的比值的范围满足：1.5～2.5。
  25. 根据权利要求1～24任一项所述的流体机械，其中所述限位通道(31)的截面为半圆形的一部分，所述滑块(40)在所述滑块(40)滑动方向上的投影包括弧线段和直线段，且所述弧形段的曲率半径的两倍为D1，所述直线段的长度为d1，D1与d1之间满足：比值d1/D1的范围为0.3～1。
  26. 根据权利要求25所述的流体机械，其中D1与d1之间满足：比值d1/D1的范围为0.5～0.7。
  27. 根据权利要求1～26任一项所述的流体机械，其中所述缸套(20)具有压缩 进气口(21)和压缩排气口(22)，
    在任一所述滑块(40)处于进气位置的情况下，所述压缩进气口(21)与对应的所述变容积腔(311)导通；
    在任一所述滑块(40)处于排气位置的情况下，对应的所述变容积腔(311)与所述压缩排气口(22)导通。
  28. 根据权利要求27所述的流体机械，其中所述挤压面(42)在所述滑块(40)滑动方向上的投影面积为S 滑块，所述缸套(20)的压缩排气口(22)的排气面积为S 排，比值S 滑块/S 排的范围为8～25。
  29. 根据权利要求28所述的流体机械，其中S 滑块/S 排的比值范围为12～18。
  30. 根据权利要求27～29任一项所述的流体机械，其中所述缸套(20)的内壁面具有吸气腔(23)，所述吸气腔(23)与所述压缩进气口(21)连通。
  31. 根据权利要求30所述的流体机械，其中所述吸气腔(23)绕所述缸套(20)的内壁面的周向延伸第一预设距离，以构成弧形吸气腔(23)。
  32. 根据权利要求31所述的流体机械，其中两个所述吸气腔(23)沿所述缸套(20)的轴向间隔设置，所述缸套(20)还具有吸气连通腔(24)，两个所述吸气腔(23)均与所述吸气连通腔(24)连通，且所述压缩进气口(21)通过所述吸气连通腔(24)与所述吸气腔(23)连通。
  33. 根据权利要求32所述的流体机械，其中所述吸气连通腔(24)沿所述缸套(20)的轴向延伸第二预设距离，所述吸气连通腔(24)的至少一端贯通所述缸套(20)的轴向端面。
  34. 根据权利要求33所述的流体机械，其中所述缸套(20)的外壁上开设有排气腔(25)，所述压缩排气口(22)由所述缸套(20)的内壁连通至所述排气腔(25)处，所述流体机械还包括排气阀组件(60)，所述排气阀组件(60)设置在所述排气腔(25)内并对应所述压缩排气口(22)设置。
  35. 根据权利要求34所述的流体机械，其中两个所述压缩排气口(22)沿所述缸套(20)的轴向间隔设置，所述排气阀组件(60)为两组，两组所述排气阀组件(60)分别对应两个所述压缩排气口(22)设置。
  36. 根据权利要求34或35所述的流体机械，其中所述缸套(20)的轴向端面上还设置有连通孔(26)，所述连通孔(26)与所述排气腔(25)连通，所述流体机械还包括法兰(50)，所述法兰(50)上设置有排气通道(51)，所述连通孔(26)与 所述排气通道(51)连通。
  37. 根据权利要求36所述的流体机械，其中所述排气腔(25)贯通至所述缸套(20)的外壁面，所述流体机械还包括排气盖板(70)，所述排气盖板(70)与所述缸套(20)连接并密封所述排气腔(25)。
  38. 根据权利要求27～37任一项所述的流体机械，其中所述流体机械是压缩机。
  39. 根据权利要求1～26任一项所述的流体机械，其中所述缸套(20)具有膨胀排气口和膨胀进气口，
    在任一所述滑块(40)处于进气位置的情况下，所述膨胀排气口与对应的所述变容积腔(311)导通；
    在任一所述滑块(40)处于排气位置的情况下，对应的所述变容积腔(311)与所述膨胀进气口导通。
  40. 根据权利要求39所述的流体机械，其中所述缸套(20)的内壁面具有膨胀排气腔，所述膨胀排气腔与所述膨胀排气口连通。
  41. 根据权利要求40所述的流体机械，其中所述膨胀排气腔绕所述缸套(20)的内壁面的周向延伸第一预设距离，以构成弧形膨胀排气腔，且所述膨胀排气腔由所述膨胀排气口处向所述膨胀进气口所在一侧延伸，所述膨胀排气腔的延伸方向与所述交叉槽结构(30)的转动方向同向。
  42. 根据权利要求41所述的流体机械，其中所述膨胀排气腔为两个，两个所述膨胀排气腔沿所述缸套(20)的轴向间隔设置，所述缸套(20)还具有膨胀排气连通腔，两个所述膨胀排气腔均与所述膨胀排气连通腔连通，且所述膨胀排气口通过所述膨胀排气连通腔与所述膨胀排气腔连通。
  43. 根据权利要求42所述的流体机械，其中所述膨胀排气连通腔沿所述缸套(20)的轴向延伸第二预设距离，所述膨胀排气连通腔的至少一端贯通所述缸套(20)的轴向端面。
  44. 根据权利要求39～43任一项所述的流体机械，其中所述流体机械是膨胀机。
  45. 一种换热设备，包括权利要求1～44任一项所述的流体机械。
PCT/CN2022/135956 2021-12-07 2022-12-01 流体机械和换热设备 WO2023103876A1 (zh)

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JPS59155580A (ja) * 1983-02-25 1984-09-04 Hitachi Ltd 容量制御型圧縮機
JP2011157921A (ja) * 2010-02-03 2011-08-18 Mitsubishi Electric Corp ２シリンダロータリ圧縮機
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59155580A (ja) * 1983-02-25 1984-09-04 Hitachi Ltd 容量制御型圧縮機
JP2011157921A (ja) * 2010-02-03 2011-08-18 Mitsubishi Electric Corp ２シリンダロータリ圧縮機
CN106438359A (zh) * 2015-08-07 2017-02-22 珠海格力节能环保制冷技术研究中心有限公司 压缩机、换热设备和压缩机的运行方法
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