WO2023226409A1 - Machine à fluide et dispositif d'échange de chaleur - Google Patents

Machine à fluide et dispositif d'échange de chaleur Download PDF

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Publication number
WO2023226409A1
WO2023226409A1 PCT/CN2022/140955 CN2022140955W WO2023226409A1 WO 2023226409 A1 WO2023226409 A1 WO 2023226409A1 CN 2022140955 W CN2022140955 W CN 2022140955W WO 2023226409 A1 WO2023226409 A1 WO 2023226409A1
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WO
WIPO (PCT)
Prior art keywords
cylinder liner
suction
slider
fluid machine
crankshaft
Prior art date
Application number
PCT/CN2022/140955
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English (en)
Chinese (zh)
Inventor
宋雪威
杜忠诚
张培林
于瑞波
李直
余冰
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 WO2023226409A1 publication Critical patent/WO2023226409A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present application relates to the technical field of heat exchange systems, specifically, to a fluid machine and heat exchange equipment.
  • Fluid machinery in related technologies includes compressors, expanders, etc. Take a compressor as an example.
  • a fluid machine including a crankshaft, a cylinder liner, a cross groove structure, a slide block and two flanges.
  • the crankshaft is provided with two eccentric parts along its axial direction; the crankshaft and the cylinder liner are eccentrically arranged And the eccentric distance is fixed; the cross-slot structure is rotatably arranged in the cylinder liner.
  • the cross-slot structure has two limit channels. The two limit channels are arranged sequentially along the axial direction of the crankshaft. The extension direction of the limit channels is perpendicular to the crankshaft.
  • the slider has a through hole, there are two sliders, the two eccentric parts extend into the two through holes of the two sliders, and the two sliders slide correspondingly and are arranged in the two limit channels and form
  • the variable volume chamber is located in the sliding direction of the slider.
  • the crankshaft rotates to drive the slider to slide back and forth in the limit channel while interacting with the cross groove structure, causing the cross groove structure and slider to rotate in the cylinder liner;
  • Two flanges are respectively provided at both axial ends of the cylinder liner.
  • Exhaust channels are provided on both flanges.
  • the two exhaust channels are respectively connected with the variable volume chambers on the corresponding sides. Among them, the channel section of the exhaust channel
  • the cross-sectional area is 0.5%-35% of the projected area of the slider in its sliding direction.
  • the projection of the slider in its sliding direction is a semicircle.
  • the axial projection of the slider in the through hole has two relatively parallel straight line segments and an arc segment connecting the ends of the two straight line segments; the position of the exhaust channel in the circumferential direction of the flange is ( Within the angle range of 90°-arccos(C/D) ⁇ 90°+arccos(C/D)), where C is the angle between two relatively parallel straight line segments of the projection of the slider in the axial direction of the through hole.
  • Distance, D is the inner diameter of the cylinder liner.
  • oblique cuts are provided on the inner circle edges of both axial ends of the cylinder liner, and the two oblique cuts are used to communicate with the two exhaust channels respectively.
  • the two exhaust channels are arranged concentrically in the axial direction of the cylinder liner, and the two oblique cuts are at the same position in the circumferential direction of the cylinder liner; or, the two exhaust channels are arranged non-concentrically in the axial direction of the cylinder liner. , the positions of the two oblique cuts in the circumferential direction of the cylinder liner are inconsistent.
  • the sum of the projected area of the oblique cut on the inner circle of the cylinder liner and the projected area of the oblique cut on the end face of the cylinder liner is greater than or equal to the cross-sectional area of the channel section of the exhaust channel.
  • a drainage groove is provided on the end face of the flange facing the cylinder liner, the drainage groove is connected with the exhaust channel, and the drainage groove is arranged opposite to and connected with the oblique cut.
  • the cylinder liner has at least one radial suction hole.
  • the radial suction hole is used to communicate with the variable volume chamber.
  • the inner wall of the cylinder liner has a suction chamber.
  • the radial suction hole communicates with the variable volume chamber through the suction chamber. The cavity is connected.
  • the suction chamber extends a first preset distance around the circumference of the inner wall surface of the cylinder liner to form an arc-shaped suction chamber.
  • the two suction chambers are spaced along the axial direction of the cylinder liner.
  • the cylinder liner also has a suction communication chamber. Both suction chambers are connected to the suction communication chamber.
  • the radial suction hole is connected to the two suction cavities 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 penetrates the axial end surface of the cylinder liner.
  • the two suction chambers are spaced along the axial direction of the cylinder liner, and there are two radial suction holes, and the two radial suction holes correspond to the two suction chambers one by one. , and the two radial suction holes are connected to the corresponding variable volume chambers through the two suction cavities.
  • one of the two flanges has an air inlet channel, and the air inlet channel and the exhaust channel on the same flange have a phase difference in the circumferential direction of the flange.
  • the cylinder liner has a radial suction hole, and the air inlet channel has a phase difference in the circumferential direction of the flange.
  • the air channel and the radial suction hole are respectively connected with the two variable volume cavities.
  • both flanges have air inlet channels, and the air inlet channel and the exhaust channel on the same flange have a phase difference in the circumferential direction of the flange, and the two air inlet channels are connected to the two variable volume cavities respectively.
  • the eccentric amounts of the two eccentric parts are equal, and there is a phase difference of the second included angle B between the extension directions of the two limiting channels, Among them, the first included angle A is twice the second included angle B.
  • the first included angle A is 160 degrees to 200 degrees; the second included angle B is 80 degrees to 100 degrees.
  • the slide block has an extrusion surface facing the end of the limiting channel, and the projected area S of the extrusion surface in the sliding direction of the slide block is in contact with the end of the cylinder liner.
  • the area of the exhaust port between rows S satisfies: the value of S slider /S row is 8 to 25.
  • a heat exchange device including a fluid machine, and the fluid machine is the above-mentioned fluid machine.
  • Figure 1 shows a schematic diagram of the internal structure of a compressor according to an optional embodiment of the present application.
  • FIG. 2 shows a schematic cross-sectional structural view of the pump body assembly of the compressor in FIG. 1 from a first perspective.
  • FIG. 3 shows an exploded structural view of the pump body assembly in FIG. 2 .
  • Figure 4 shows a schematic diagram of the assembly structure of the crankshaft, cross groove structure, and slide block in Figure 3.
  • FIG. 5 shows a schematic cross-sectional structural view of the crankshaft, cross groove structure, and slide block in FIG. 4 .
  • FIG. 6 shows a schematic cross-sectional structural view of the pump body assembly of the compressor in FIG. 1 from a second perspective.
  • FIG. 7 shows a schematic cross-sectional structural view from the E-E perspective in FIG. 6 .
  • FIG. 8 shows a schematic structural view of an optional embodiment of the upper flange of the pump body assembly in FIG. 3 .
  • Fig. 9 shows a schematic structural view of the upper flange of the pump body assembly in Fig. 3 having a drainage groove.
  • FIG. 10 shows an enlarged structural schematic diagram of F in FIG. 9 .
  • FIG. 11 shows a schematic cross-sectional structural view of the exhaust channel and the guide groove of the upper flange in FIG. 9 .
  • FIG. 12 shows a schematic structural diagram of an optional embodiment of the lower flange of the pump body assembly in FIG. 3 .
  • Figure 13 shows a schematic structural diagram of the lower flange of the pump body assembly in Figure 3 having a drainage groove.
  • FIG. 14 shows an enlarged structural schematic diagram of G in FIG. 13 .
  • FIG. 15 shows a schematic cross-sectional structural view of the exhaust channel and the guide groove of the lower flange in FIG. 13 .
  • FIG. 16 shows a schematic structural view of the angular position of the exhaust channel of the upper flange in the circumferential direction of the upper flange in FIG. 3 .
  • FIG. 17 shows a schematic structural view of the angular position of the exhaust channel of the lower flange in the circumferential direction of the lower flange in FIG. 3 .
  • FIG. 18 shows a schematic structural view of the cylinder liner of the pump body assembly in FIG. 3 .
  • Figure 19 shows a schematic structural view of the upper flange, cylinder liner and lower flange of the pump body assembly in Figure 3 in an exploded state.
  • Figure 20 shows a schematic structural diagram of the single suction of the cylinder liner of the pump body structure according to Embodiment 1 of the present application.
  • Figure 21 shows a schematic structural diagram of the double suction of the cylinder liner of the pump body structure according to Embodiment 2 of the present application.
  • Figure 22 shows a schematic structural diagram of the upper flange and lower flange suction of the pump body structure according to Embodiment 3 of the present application.
  • Figure 23 shows a schematic structural diagram of the single suction of the cylinder liner and the single suction of the flange of the pump body structure according to Embodiment 4 of the present application.
  • FIG. 24 shows a schematic structural diagram of the shaft body part of the crankshaft in FIG. 3 and the eccentricity of the two eccentric parts.
  • FIG. 25 shows a schematic cross-sectional structural view of the assembly eccentricity of the crankshaft and cylinder liner in FIG. 3 .
  • Figure 26 shows a schematic structural diagram of the eccentricity between the cylinder liner and the lower flange in Figure 3.
  • FIG. 27 shows a schematic structural view of the slider in FIG. 3 in the axial direction of the through hole.
  • Figure 28 shows a schematic diagram of the mechanism of compressor operation according to an optional embodiment of the present application.
  • Fig. 29 shows a schematic diagram of the mechanism of the operation of the compressor in Fig. 28.
  • Figure 30 shows a schematic diagram of the mechanism of compressor operation in the related art.
  • Figure 31 shows a schematic diagram of the mechanism of the improved compressor operation in the related art.
  • Figure 32 shows a schematic diagram of the mechanism of the operation of the compressor in Figure 31. In this figure, the force arm of the drive shaft driving the slider to rotate is shown.
  • Figure 33 shows a schematic diagram of the mechanism of operation of the compressor in Figure 31.
  • the center of the limiting groove structure coincides with the center of the eccentric portion.
  • a compressor operating mechanism principle is proposed based on the cross slider mechanism, that is, point O1 is used as the cylinder center, point O2 is used as the drive shaft center, and point O3 is used as the slider center.
  • the cylinder and the drive shaft are eccentrically arranged, in which the slider center O 3 makes a circular motion on a circle with a diameter O 1 O 2 .
  • the cylinder center O 1 and the drive shaft center O 2 serve as the two rotation centers of the motion mechanism.
  • the midpoint O 0 of the line segment O 1 O 2 serves 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 motion mechanism with O 0 as the center of the drive shaft that is, the cylinder center O 1 and the drive shaft center O 0 are the two rotation centers of the motion mechanism.
  • the drive shaft has an eccentric part, the slider and the eccentric part are coaxially arranged, and the drive shaft is 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 mechanism including a cylinder, a limit groove structure, a slider and a drive shaft.
  • 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 moves reciprocally relative to the limit groove structure.
  • the slider is coaxially assembled with the eccentric part of the drive shaft.
  • the slider makes circular motion around the shaft part of the drive shaft.
  • 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 limiter.
  • Bit slot structure rotation 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
  • this application proposes a new cross-slot structure with two limit channels and a double slider mechanism principle, and builds a new compressor based on this principle, which has high energy efficiency and low noise.
  • the compressor takes the compressor as an example to introduce in detail the fluid machinery based on the cross-groove structure with two limit channels and double sliders.
  • this application provides a fluid machinery and heat exchange equipment, wherein , the heat exchange equipment includes fluid machinery, and the fluid machinery is the fluid machinery described above and below.
  • the fluid machine in the embodiment of the present application includes a crankshaft 10, a cylinder liner 20, a cross groove structure 30 and a slider 40.
  • the crankshaft 10 is provided with two eccentric parts 11 along its axial direction, and there is a third eccentric part 11 between the two eccentric parts 11. With a phase difference of an included angle A, the eccentricities of the two eccentric parts 11 are equal; the crankshaft 10 and the cylinder liner 20 are eccentrically arranged and the eccentric distance is fixed; the cross-slot structure 30 is rotatably disposed in the cylinder liner 20, and the cross-slot structure 30 has Two limiting channels 31 are arranged sequentially along the axial direction of the crankshaft 10 .
  • the extending direction of the limiting channels 31 is perpendicular to the axial direction of the crankshaft 10 , and the extending direction of the two limiting channels 31 is between There is a phase difference of the second included angle B, where 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 two eccentric parts 11 extend in accordingly
  • the two slide blocks 40 are slidably arranged in the two limiting channels 31 and form a variable volume cavity.
  • the variable volume cavity is located in the sliding direction of the slide blocks 40, and the crankshaft 10 rotates.
  • the slide block 40 is driven to slide back and forth in the limiting channel 31 while interacting with the cross groove structure 30 so that the cross groove structure 30 and the slide block 40 rotate in the cylinder liner 20 .
  • the two eccentric parts 11 of the crankshaft extend into the two through holes 41 of the two slide blocks 40 correspondingly.
  • the two sliders 40 are slidably arranged in the two limiting channels 31 and form a variable volume cavity, because the first included angle A between the two eccentric parts 11 is one of the extending directions of the two limiting channels 31 In this way, when one of the two sliders 40 is at the dead center position, that is, the driving torque of the eccentric portion 11 corresponding to the slider 40 at the dead center position is 0, the slider 40 at the dead center position cannot continue to rotate, and at this time, the driving torque of the other of the two eccentric parts 11 driving the corresponding slider 40 is the maximum value, ensuring the maximum driving torque.
  • the eccentric part 11 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 center position to continue to rotate through the cross groove structure 30, realizing fluid flow.
  • the stable operation of the machinery avoids the dead center position of the movement mechanism, improves the movement reliability of the fluid machinery, and ensures the working reliability of the heat exchange equipment.
  • the fluid machinery provided by the embodiments of the present application can operate stably, that is, it ensures that the energy efficiency of the compressor is high and the noise is low, thereby ensuring the working reliability of the heat exchange equipment.
  • neither the first included angle A nor the second included angle B is zero.
  • crankshaft 10 rotates around the axis O 0 of the crankshaft 10; the cross groove structure 30 revolves around the axis O 0 of the crankshaft 10, and the axis O 0 of the crankshaft 10
  • the first slider 40 makes a circular motion with the axis O0 of the crankshaft 10 as the center, and the center O3 of the first slider 40 is in contact with the crankshaft.
  • the distance between the axis O 0 of the crankshaft 10 is equal to the eccentricity of the first eccentric portion 11 corresponding to the crankshaft 10 , and the eccentricity is equal to the eccentricity between the axis O 0 of the crankshaft 10 and the axis O 1 of the cross groove structure 30 distance, the crankshaft 10 rotates to drive the first slider 40 to perform circular motion, and the first slider 40 interacts with the cross groove structure 30 and slides back and forth in the limiting channel 31 of the cross groove structure 30; the second slider The block 40 makes a circular motion with the axis O 0 of the crankshaft 10 as the center, and the distance between the center O 4 of the second slide block 40 and the axis O 0 of the crankshaft 10 is equal to the corresponding second eccentric part 11 of the crankshaft 10
  • the eccentricity is equal to the eccentricity distance between the axis O 0 of the crankshaft 10 and the axis O 1 of the cross groove structure 30 .
  • the crankshaft 10 rotates to drive the second slider
  • the fluid machine operated as described above constitutes a cross slider mechanism.
  • This operating method adopts the principle of the cross slider mechanism, in which the two eccentric parts 11 of the crankshaft 10 serve as the first connecting rod L 1 and the second connecting rod L 2 respectively.
  • the two limiting channels 31 of the cross groove structure 30 serve as the third link L 3 and the fourth link L 4 respectively, and the lengths of the first link L 1 and the second link L 2 are equal (please refer to Figure 28 ).
  • first included angle A between the first link L 1 and the second link L 2
  • second included angle B between the third link L 3 and the fourth link L 4 .
  • the first included angle A is twice the second included angle B.
  • connection between the axis O 0 of the crankshaft 10 and the axis O 1 of the cross groove structure 30 is the connection line O 0 O 1 , and the connection between the first connecting rod L 1 and the connection line O 0 O 1
  • connection line O 0 O 1 There is a third included angle C between them, and there is a fourth included angle D between the corresponding third connecting rod L 3 and the connection line O 0 O 1 , where the third included angle C is twice the fourth included angle D
  • there is a sixth included angle F between the corresponding fourth connecting rod L 4 and the connecting line O 0 O 1 where the fifth included angle Angle E is twice the sixth included angle F
  • the sum of the third included angle C and the fifth included angle E is the first included angle A
  • sum of the fourth included angle D and the sixth included angle F is the second included angle B.
  • the operation method also includes that the rotation angular speed of the slider 40 relative to the eccentric portion 11 is the same as the revolution angular speed of the slider 40 around the axis O 0 of the crankshaft 10 ; the revolution angular speed of the cross groove structure 30 around the axis O 0 of the crankshaft 10 This is the same as the rotation angular speed of the slider 40 relative to the eccentric portion 11 .
  • the axis O 0 of the crankshaft 10 is equivalent to the rotation center of the first connecting rod L 1 and the second connecting rod L 2
  • the axis O 1 of the cross groove structure 30 is equivalent to the third connecting rod L 3 and the fourth connecting rod L 3
  • the rotation center of connecting rod L 4 ; the two eccentric portions 11 of the crankshaft 10 serve as the first connecting rod L 1 and the second connecting rod L 2 respectively
  • the two limiting channels 31 of the cross groove structure 30 serve as the third connecting rod L respectively.
  • 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.
  • the eccentric portion 11 on the crankshaft 10 drives the corresponding slider 40 around the crankshaft.
  • the axis O of 10 revolves at 0 , and at the same time the slider 40 can rotate relative to the eccentric part 11, and the relative rotation speed of the two is the same. Since the first slider 40 and the second slider 40 are in two corresponding limits respectively, The reciprocating movement in the position channel 31 drives the cross groove structure 30 to perform circular motion. Limited by the two limiting channels 31 of the cross groove structure 30, the movement direction of the two slide blocks 40 always has the phase of the second included angle B.
  • the eccentric part 11 used to drive the other of the two sliders 40 has the maximum driving torque, and the eccentric part 11 with the maximum driving torque can
  • the corresponding slider 40 is normally driven to rotate, thereby driving the cross groove structure 30 to rotate through the slider 40, and then driving the slider 40 at the dead center position to continue to rotate through the cross groove structure 30, achieving stable operation of the fluid machinery. It avoids the dead center position of the motion mechanism and improves the motion reliability of the fluid machinery, thus ensuring the working reliability of the heat exchange equipment.
  • 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 has 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 suction and exhaust processes.
  • the fluid machine also includes a flange 50.
  • the flange 50 is arranged at the axial end of the cylinder liner 20.
  • the crankshaft 10 and the flange 50 are arranged concentrically.
  • the cross groove structure 30 is concentric with the cylinder liner 20. Shaft setting, the assembly eccentricity of the crankshaft 10 and the cross groove structure 30 is determined by the relative positional relationship between the flange 50 and the cylinder liner 20.
  • the flange 50 is fixed on the cylinder liner 20 through the fastener 90, and the axis of the flange 50 The relative position to the axis of the inner ring of the cylinder liner 20 is controlled by the alignment of the flange 50 .
  • the relative position of the axis of the flange 50 to 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 essence of the relative position of the axis center through the flange 50 is to make the eccentricity of the eccentric portion 11 equal to the assembly eccentricity of the crankshaft 10 and the cylinder liner 20 .
  • the eccentricities of the two eccentric parts 11 are equal to e.
  • the assembly eccentricity between the crankshaft 10 and the cylinder liner 20 is e (due to the cross groove structure 30 and the cylinder liner 20 is coaxially arranged, the assembly eccentricity between the crankshaft 10 and the cross groove structure 30 is the assembly eccentricity between the crankshaft 10 and the cylinder liner 20), the flange 50 includes an upper flange 52 and a lower flange 53, as shown in Figure 26 As shown, the distance between the inner ring axis of the cylinder liner 20 and the inner ring axis of the lower flange 53 is e, that is, equal to the eccentricity of the eccentric portion 11 .
  • first assembly gap between the crankshaft 10 and the flange 50, and the first assembly gap ranges from 0.005mm to 0.05mm.
  • the first assembly gap ranges from 0.01 to 0.03 mm.
  • the two slide blocks 40 are respectively arranged concentrically with the two eccentric parts 11.
  • the slide blocks 40 make circular motion around the axis of the crankshaft 10.
  • the first rotation gap ranges from 0.005mm to 0.05mm.
  • the size of the second rotation gap is 0.005 mm to 0.1 mm.
  • the shaft body portion 12 of the crankshaft 10 is integrally formed, and the shaft body portion 12 has only one axis center. This facilitates the one-time molding of the shaft portion 12 , thereby reducing the difficulty of processing and manufacturing the shaft portion 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 coaxially arranged, and the two eccentric portions 11 Set on the first and second paragraphs respectively.
  • first section and the second section are removably connected. In this way, the convenience of assembly and disassembly of the crankshaft 10 is ensured.
  • the shaft body portion 12 of the crankshaft 10 and the eccentric portion 11 are integrally formed. This facilitates the one-time molding of the crankshaft 10 , thereby reducing the difficulty of processing and 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 part 11 is facilitated.
  • both ends of the limiting channel 31 penetrate to the outer peripheral surface of the cross groove structure 30 . In this way, it is helpful to reduce the difficulty of processing and manufacturing the cross groove structure 30 .
  • the first included angle A is 160 degrees to 200 degrees; the second included angle B is 80 degrees to 100 degrees. In this way, as long as the relationship that the first included angle A is twice the second included angle B is satisfied.
  • 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
  • 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
  • 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, 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 effective driving force on the slider 40 , thereby ensuring the movement reliability 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 body portion 12 of the crankshaft 10 .
  • the proximal end of the eccentric portion 11 protrudes from the outer circle of the shaft body portion 12 of the crankshaft 10 .
  • the proximal end of the eccentric portion 11 is located inside the outer circle of the shaft body portion 12 of the crankshaft 10 .
  • the slider 40 includes a plurality of substructures, and the plurality of substructures are spliced to form a through hole 41 .
  • the two eccentric portions 11 are spaced apart in the axial direction of the crankshaft 10 .
  • the cylinder liner 20 and the two slide blocks 40 it is ensured that the distance between the two eccentric portions 11 can provide an assembly space for the cylinder liner 20 to ensure ease of assembly.
  • the cross groove structure 30 has a central hole 32 , and the two limiting channels 31 are connected through the central hole 32 .
  • the diameter of the central hole 32 is larger than the diameter of the shaft body portion 12 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 pass through the center hole 32 smoothly.
  • the axial projection of the slider 40 in 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 limiting channel 31 has a set of oppositely arranged first sliding surfaces that are in sliding contact with the slider 40 .
  • the slider 40 has a second sliding surface that cooperates with the first sliding surface.
  • the slider 40 has a surface facing the limiting channel 31
  • the extrusion surface 42 at the end serves as the head of the slider 40.
  • the two second sliding surfaces are connected through the extrusion surface 42, and the extrusion surface 42 faces the variable volume cavity.
  • the projection of the second sliding surface of the slider 40 in the axial direction of the through hole 41 is a straight line segment, and at the same time, the projection of the pressing surface 42 of the slider 40 in the axial direction of the 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 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.
  • the X dashed line represents 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 radius of curvature of the arc surface and the radius of the inner circle of the cylinder liner 20 have a difference, and the difference ranges from -0.05mm to 0.025mm.
  • the difference range is -0.02 ⁇ 0.02mm.
  • the projected area S of the extrusion surface 42 in the sliding direction of the slider 40 slider and the area S row of the compression exhaust port 22 of the cylinder liner 20 satisfy: the value of S slider /S row is 8 ⁇ 25.
  • the value of S slider /S row is 12 ⁇ 18.
  • the fluid machine shown in this embodiment is a compressor.
  • the compressor includes a liquid dispenser component 80, a housing component 81, a motor component 82, a pump body component 83, an upper cover component 84 and a lower cover component 85.
  • the dispenser component 80 is arranged outside 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
  • the motor assembly 82 and the pump body assembly 83 They are all located inside the housing assembly 81 , where 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 above-mentioned crankshaft 10, cylinder liner 20, cross groove structure 30, slide block 40, upper flange 52 and lower flange 53.
  • the above components are connected by welding, thermal sheathing, 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 slide blocks 40 are respectively placed in the two corresponding limit channels 31, and the two eccentric parts 11 of the crankshaft 10 are respectively extended into In the two corresponding through holes 41 of the two slide blocks 40, place the assembled crankshaft 10, the cross groove structure 30 and the two slide blocks 40 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 disposed through the upper flange 52, see Figures 2 and 3 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.
  • the pump body assembly 83 has a total of 4 variable volume chambers. In the volume chamber, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 times, and a single variable volume chamber completes one suction and exhaust process. For the compressor, the crankshaft 10 rotates 2 times, completing a total of 4 suction and exhaust processes.
  • extrusion surface 42 of the head of the slider 40 , the two side wall surfaces and the bottom surface of the passage 31 , part of the inner wall surface of the cylinder liner 20 , and part of the surface of the upper flange 52 facing the cylinder liner 20 (or part of the surface of the lower flange 53 facing the cylinder liner 20 side) is a variable volume chamber.
  • the motor assembly 82 drives the crankshaft 10 to rotate, and the two eccentric portions 11 of the crankshaft 10 drive the corresponding two slide blocks 40 to move.
  • the slide blocks 40 revolve around the axis of the crankshaft 10
  • the slide blocks 40 Rotates relative to the eccentric part 11, and the slider 40 reciprocates along the limit channel 31, and drives the cross groove structure 30 to rotate in the cylinder liner 20. While the slider 40 revolves, it reciprocates along the limit channel 31 to form a cross slide. Block mechanism movement mode.
  • this application sets two exhaust channels 51 on two flanges 50 respectively, so that the exhaust channels 51 are smaller than the relevant cylinder liner. 20
  • the exhaust on the side wall is improved to a flat exhaust structure, as follows:
  • the fluid machine includes two flanges 50.
  • the two flanges 50 are respectively provided at both axial ends of the cylinder liner 20. Both flanges 50 are provided with exhaust passages 51.
  • Each exhaust channel 51 is respectively connected with the variable volume cavity on the corresponding side; wherein, the cross-sectional area of the channel section of the exhaust channel 51 is 0.5%-35% of the projected area of the slider 40 in its sliding direction.
  • exhaust passages 51 By opening exhaust passages 51 on both flanges 50, and at the same time, the two exhaust passages 51 are respectively connected with the variable volume chambers on the corresponding sides. In this way, since the exhaust passages 51 are opened on the plane of the flange 50 , compared with the related opening on the side wall arc surface of the cylinder liner 20, it is beneficial to reduce the problems caused by the edges and corners of the exhaust passage 51 and the uneven assembly of the cylinder liner 20 and the flange 50 during the assembly process.
  • the exhaust path of the compressor is changed to avoid the generation of noise; in addition, since the exhaust channel 51 is opened on the plane of the flange 50 and belongs to the outer plane, compared with the exhaust channel 51 opened on the cylinder liner 20 As for the side wall arc surface, the processing difficulty of the exhaust channel 51 is greatly reduced, and the processing of the parts is relatively easier, which is beneficial to polishing flanges or burrs caused by processing.
  • both ends in the length direction of the exhaust passage 51 of the compressor provided by the present application are flat, therefore, under the condition that the bearing thickness and the diameter of the exhaust passage 51 are the same, the flat exhaust passage of the present application
  • the 51 is smaller in size and has smaller clearance volume, which is beneficial to ensuring cooling capacity and reducing power consumption.
  • exhaust loss can be avoided by reasonably optimizing the ratio of the cross-sectional area of the exhaust channel 51 and the projected area of the slider 40 in its sliding direction.
  • the gas compressed by the upper compression chamber is discharged through the upper flange 52, and the gas compressed by the lower compression chamber is discharged through the lower flange 53.
  • the upper and lower compression chambers and the two exhaust channels 51 are independent of each other and do not affect each other, which is beneficial to This prevents the gases in the two compression chambers from interacting with each other and generating noise such as pulsation due to the exhaust through the cylinder liner 20 side.
  • the related exhaust gas on the cylinder liner 20 side is indirect exhaust, that is, after the gas is discharged, it first passes through the exhaust port of the cylinder liner 20 and then enters the exhaust chamber of the cylinder liner 20, and then flows to the method through the suction connecting chamber on the cylinder liner 20. flange 50, and finally discharged from the flange 50.
  • the entire exhaust process passes through the corners or uneven edges left during the assembly of each part, which is easy to generate noise.
  • the two flanges 50 provided by this application pass through Exhaust through the exhaust channel 51 is direct exhaust, and the gas is directly discharged into the casing.
  • the exhaust path is short and turbulent airflow is less likely to occur.
  • the projection of the slider 40 in its sliding direction is a semicircle.
  • the axial projection of the slider 40 in the through hole 41 has two A relatively parallel straight line segment and an arc segment connecting the ends of the two straight line segments.
  • the position of the exhaust channel 51 of the assembled upper flange 52 in the circumferential direction of the upper flange 52, and the angle at which the upper slider 40 starts to inhale is the 0° baseline.
  • the hour hand rotation angle is positive, and the position of the exhaust channel 51 in the circumferential direction of the upper flange 52 is within the angle range of (90°-arccos(C/D) ⁇ 90°+arccos(C/D)), where, C is the distance between two relatively parallel straight lines of the projection of the slider 40 in the axial direction of the through hole 41 , and D is the inner diameter of the cylinder liner 20 .
  • the exhaust channel 51 of the assembled lower flange 53 is positioned in the circumferential direction of the lower flange 53.
  • the angle at which the lower slider 40 starts to inhale is the 0° baseline and rotates clockwise. The angle is positive, and the setting position of the exhaust channel 51 in the circumferential direction of the lower flange 53 is within the angle range of (90°-arccos(C/D) ⁇ 90°+arccos(C/D)), where C is the sliding
  • C is the sliding
  • the distance D between two relatively parallel straight line segments of the axial projection of the block 40 in the through hole 41 is the inner diameter of the cylinder liner 20 .
  • oblique cuts 27 are provided at the inner circumferential edges of both axial ends of the cylinder liner 20 , and the two oblique cuts 27 are respectively used to communicate with the two exhaust passages 51 .
  • the arrangement of the oblique cuts 27 is beneficial to increasing the gas flow path, thereby reducing the exhaust loss.
  • the two exhaust passages 51 are concentrically arranged in the axial direction of the cylinder liner 20 , and the two oblique cuts 27 are at the same position in the circumferential direction of the cylinder liner 20 .
  • the two exhaust passages 51 are disposed non-concentrically in the axial direction of the cylinder liner 20 , and the positions of the two oblique cuts 27 in the circumferential direction of the cylinder liner 20 are inconsistent.
  • the sum of the projected area of the oblique cut 27 on the inner circle of the cylinder liner 20 and the projected area of the oblique cut 27 on the end face of the cylinder liner 20 is greater than or equal to the cross-sectional area of the exhaust channel 51 . In this way, it is helpful to increase the flow path of gas, thereby reducing exhaust loss.
  • a drainage groove 58 is provided on the end face of the flange 50 facing the cylinder liner 20 .
  • the drainage groove 58 is connected with the exhaust channel 51 , and the drainage groove 58 is connected with the oblique cutout 27 Relatively set up and connected. In this way, while reducing over-compression and power consumption, it also functions as a resonant cavity.
  • FIG. 8 there is a schematic structural diagram of the upper flange 52 without a drainage groove 58 ; as shown in FIGS. 9 to 11 , the upper flange 52 has a drainage groove on the end face facing the cylinder liner 20 58 structural diagram.
  • FIG 12 there is a schematic structural diagram of the lower flange 53 without the drainage groove 58; as shown in Figures 13 and 14, the upper flange 52 has a drainage groove on the end face facing the cylinder liner 20. 58 structural diagram.
  • the cylinder liner 20 has at least one radial suction hole 21, which is used to communicate with the variable volume chamber.
  • the inner wall surface of the cylinder liner 20 has a suction chamber 23, and the radial suction hole 21 It communicates with the variable volume chamber through the suction chamber 23.
  • the suction chamber 23 can store a large amount of gas, so that the variable volume chamber can be filled with suction, so that the compressor can suction a sufficient amount, and when suction is insufficient, the stored gas can be supplied to the compressor in time.
  • Variable volume chamber to ensure the compression efficiency of the compressor.
  • the compressor suction is sufficient, and the performance and cooling capacity of the compressor can be improved. It can solve the problem of mutual interference of various structures during design due to the compact structure of the pump body assembly 83, making the design easier.
  • the suction chamber 23 is a cavity formed by being hollowed out in the radial direction on the inner wall surface of the cylinder liner 20. There may be one suction chamber 23, or there may be two upper and lower suction chambers.
  • the suction chamber 23 extends a first preset distance around the circumference of the inner wall surface of the cylinder liner 20 to form an arc-shaped suction chamber 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 two suction chambers 23 are spaced apart along the axial direction of the cylinder liner 20.
  • the cylinder liner 20 also has a suction communication chamber 24. Both of the two suction chambers 23 are connected to the suction chamber.
  • the air communication chamber 24 is connected.
  • the radial suction hole 21 is connected with the two suction chambers 23 through the suction communication chamber 24. In this way, it is beneficial to increase the volume of the suction chamber 23, thereby reducing the suction pressure pulsation.
  • 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 penetrates 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.
  • the two suction chambers 23 are spaced apart along the axial direction of the cylinder liner 20.
  • the two radial suction holes 21 are connected to the two radial suction holes 21.
  • the suction cavities 23 correspond one to one, and the two radial suction holes 21 are connected to the corresponding variable volume chambers through the two suction cavities 23 respectively.
  • one of the two flanges 50 has an air inlet passage 54, and the air inlet passage 54 and the exhaust passage 51 on the same flange 50 have a phase difference in the circumferential direction of the flange 50.
  • the cylinder liner 20 It has a radial suction hole 21, and the air inlet passage 54 and the radial suction hole 21 are respectively connected with two variable volume chambers.
  • both flanges 50 have air inlet passages 54, and the air inlet passage 54 and the exhaust passage 51 on the same flange 50 have a phase difference in the circumferential direction of the flange 50.
  • the two air inlet passages 54 is connected with two variable volume cavities respectively.
  • both flanges 50 are connected to the cylinder liner 20 through fasteners 90 .
  • spatially relative terms can be used here, such as “on", “on", “on the upper surface of", “above”, etc., to describe what is shown in the figure.
  • the exemplary term “over” may include both orientations “above” and “below.”
  • the device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Machine à fluide et dispositif d'échange de chaleur. La machine à fluide comprend un vilebrequin (10), un revêtement interne (20), une structure de rainure transversale (30), un bloc coulissant (40) et deux brides (50). Deux parties excentriques (11) sont disposées dans la direction axiale du vilebrequin (10). Le vilebrequin (10) et le revêtement interne (20) sont agencés de manière excentrique avec une distance excentrique fixe. La structure de rainure transversale (30) est agencée en rotation dans le revêtement interne (20). Les deux parties excentriques (11) s'étendent dans les deux trous traversants correspondants (41) des deux blocs coulissants (40). Des canaux d'échappement (51) sont formés dans les deux brides (50). Les deux canaux d'échappement (51) sont respectivement en communication avec les cavités à volume variable sur les côtés correspondants. La surface de section transversale du canal d'échappement (51) est de 0,5 % à 35 % de la zone de projection du bloc coulissant (40) dans la direction de coulissement de celle-ci. Dans la machine à fluide, les canaux d'échappement sont agencés sur la bride pour abaisser le bruit et réduire la difficulté de traitement.
PCT/CN2022/140955 2022-05-23 2022-12-22 Machine à fluide et dispositif d'échange de chaleur WO2023226409A1 (fr)

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CN202210563914.3 2022-05-23
CN202210563914.3A CN117145766A (zh) 2022-05-23 2022-05-23 流体机械和换热设备

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Citations (5)

* 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
CN105987004A (zh) * 2015-01-28 2016-10-05 珠海格力节能环保制冷技术研究中心有限公司 滑片式压缩机及其排气结构
WO2017024866A1 (fr) * 2015-08-07 2017-02-16 珠海格力节能环保制冷技术研究中心有限公司 Compresseur, appareil échangeur de chaleur et procédé de commande pour un compresseur
CN111963435A (zh) * 2020-07-24 2020-11-20 珠海格力电器股份有限公司 一种压缩机和空调器
CN113638883A (zh) * 2021-09-23 2021-11-12 珠海格力节能环保制冷技术研究中心有限公司 泵体组件、压缩机和空调器

Patent Citations (5)

* 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
CN105987004A (zh) * 2015-01-28 2016-10-05 珠海格力节能环保制冷技术研究中心有限公司 滑片式压缩机及其排气结构
WO2017024866A1 (fr) * 2015-08-07 2017-02-16 珠海格力节能环保制冷技术研究中心有限公司 Compresseur, appareil échangeur de chaleur et procédé de commande pour un compresseur
CN111963435A (zh) * 2020-07-24 2020-11-20 珠海格力电器股份有限公司 一种压缩机和空调器
CN113638883A (zh) * 2021-09-23 2021-11-12 珠海格力节能环保制冷技术研究中心有限公司 泵体组件、压缩机和空调器

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