WO2023226411A1 - 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
WO2023226411A1
WO2023226411A1 PCT/CN2022/140975 CN2022140975W WO2023226411A1 WO 2023226411 A1 WO2023226411 A1 WO 2023226411A1 CN 2022140975 W CN2022140975 W CN 2022140975W WO 2023226411 A1 WO2023226411 A1 WO 2023226411A1
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WO
WIPO (PCT)
Prior art keywords
exhaust
cylinder liner
suction
fluid machine
chamber
Prior art date
Application number
PCT/CN2022/140975
Other languages
English (en)
French (fr)
Inventor
杜忠诚
任丽萍
张荣婷
丁宁
马聪聪
丁少鹏
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 WO2023226411A1 publication Critical patent/WO2023226411A1/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
    • 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. At least one of the two flanges has an air inlet passage.
  • the air inlet passage is used to communicate with the variable volume chamber.
  • the air inlet passage includes radial suction pipes that are connected in sequence. Air holes and axial suction holes, wherein the ratio S/V of the cross-sectional area S of the hole section of the radial suction hole to the displacement V of the fluid machine ranges from 0.006 to 0.01.
  • the inner wall surface of the cylinder liner is provided with an air suction chamber, and the air inlet passage is connected to the variable volume chamber through the air suction chamber.
  • 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 cavities are spaced along the axial direction of the cylinder liner.
  • the cylinder liner also has a suction communication cavity, and the two suction cavities are The suction cavities are all connected with the suction communication cavity, and the air inlet passage is connected with the suction cavity through the suction communication cavity.
  • the suction communication chamber extends a second preset distance along the axial direction of the cylinder liner, and the suction communication chamber penetrates the axial end surface of the cylinder liner toward one end of the flange with the air inlet passage.
  • the two suction chambers are spaced along the axial direction of the cylinder liner.
  • the cylinder liner also has two suction communication chambers, two The suction chamber is respectively connected with the two suction communication cavities, and the two air inlet channels are respectively connected with the suction chamber on the corresponding side through the suction communication cavity on the corresponding side.
  • the suction communication chamber extends a third preset distance along the axial direction of the cylinder liner, and one end of the suction communication chamber facing the flange on the corresponding side penetrates the axial end surface of the cylinder liner.
  • the two suction cavities are spaced along the axial direction of the cylinder liner.
  • the cylinder liner also has a suction connecting cavity, and the two suction cavities The cavities are all connected with the suction communication cavity, and the air inlet channel is connected with the suction cavity through the suction communication cavity.
  • the suction communication chamber extends a fourth preset distance along the axial direction of the cylinder liner, and both ends of the suction communication chamber penetrate through the two axial end surfaces of the cylinder liner respectively.
  • exhaust channels are provided on the end surfaces of the two flanges, and the two exhaust channels are respectively connected with the variable volume chambers on the corresponding sides.
  • the end of the air intake channel is a compression air inlet
  • the initial end of the exhaust channel is a compression exhaust port.
  • the fluid machinery is a compressor.
  • the end of the air inlet channel is an expansion exhaust port
  • the initial end of the exhaust channel is an expansion air inlet.
  • the fluid machinery is an expander.
  • an exhaust chamber is provided on the outer wall of the cylinder liner, and the cylinder liner also has an exhaust port.
  • the exhaust port is connected to the exhaust chamber from the inner wall of the cylinder liner.
  • the fluid machine also includes an exhaust valve assembly, and the exhaust valve The component is arranged in the exhaust cavity and corresponding to the exhaust port.
  • the two exhaust ports are spaced along the axial direction of the cylinder liner.
  • a communication hole is provided on at least one axial end face of the cylinder liner.
  • the communication hole is connected with the exhaust chamber, and an exhaust hole is provided on the flange of the two flanges opposite to the communication hole.
  • the channel, the connecting hole is connected with the exhaust channel.
  • the two exhaust ports are arranged at intervals along the axial direction of the cylinder liner.
  • the air valve assembly is composed of two groups, and the two groups of exhaust valve assemblies are respectively provided corresponding to the two exhaust ports.
  • the two exhaust chambers are connected through an exhaust communication port, and a communication hole is also provided on at least one axial end face of the cylinder liner.
  • the communication hole is connected to the exhaust chamber, and the flange of the two flanges is opposite to the communication hole.
  • An exhaust channel is provided on the orchid, and the connecting hole is connected with the exhaust channel.
  • the two exhaust chambers are not connected, and communication holes are provided on both axial end faces of the cylinder liner.
  • the two communication holes are connected to the two exhaust chambers respectively, and the two flanges are opposite to the communication holes.
  • Exhaust channels are provided everywhere, and the connecting holes are connected with the exhaust channels.
  • At least one exhaust port is connected to the variable volume chamber on the corresponding side.
  • At least one axial end face of the cylinder liner is also provided with a communication hole, and the communication hole is connected to the exhaust chamber.
  • Two flanges A first exhaust channel is provided on the flange opposite to the communication hole, and the communication hole is connected with the first exhaust channel; among the two flanges, the flange on the side far from the exhaust port has a second exhaust channel, and the second exhaust channel is connected to the first exhaust channel.
  • the exhaust channel is connected with the variable volume cavity on the corresponding side.
  • the exhaust chamber extends through the outer wall of the cylinder liner, and the fluid machine also includes an exhaust cover plate, which is connected to the cylinder liner and seals the exhaust chamber.
  • the end of the air intake channel is a compression air inlet
  • the exhaust port on the cylinder liner is a compression exhaust port.
  • the compression air inlet is connected to the variable volume chamber on the corresponding side.
  • the fluid machinery is a compressor.
  • the end of the air intake channel is an expansion exhaust port
  • the exhaust port on the cylinder liner is an expansion air inlet.
  • the expansion exhaust port is connected to the variable volume chamber on the corresponding side.
  • the fluid machinery is an expander.
  • 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.
  • 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 Embodiment 1 of the present application.
  • FIG. 2 shows an exploded structural view of the pump body assembly of the compressor in FIG. 1 .
  • Figure 3 shows a schematic diagram of the assembly structure of the crankshaft, cross groove structure, and slide block in Figure 2.
  • FIG. 4 shows a schematic cross-sectional structural view of the crankshaft, cross groove structure, and slide block in FIG. 3 .
  • FIG. 5 shows a schematic structural diagram of the shaft body part of the crankshaft in FIG. 2 and the eccentricity of the two eccentric parts.
  • FIG. 6 shows a schematic cross-sectional structural view of the assembly eccentricity of the crankshaft and cylinder liner in FIG. 2 .
  • Figure 7 shows a structural schematic diagram of the eccentricity between the cylinder liner and the lower flange in Figure 2.
  • Figure 8 shows a schematic structural view of the slider in Figure 2 in the axial direction of the through hole.
  • FIG. 9 shows a schematic structural diagram of the suction structure of the upper flange of the pump body assembly of the compressor in FIG. 1 .
  • Figure 10 shows a schematic structural diagram of the air suction path of the upper flange of the pump body assembly in Figure 9.
  • FIG. 11 shows a schematic cross-sectional structural diagram from the perspective of C-C in FIG. 9 .
  • FIG. 12 shows a schematic cross-sectional structural diagram from the D-D perspective in FIG. 9 .
  • Figure 13 shows a schematic structural diagram of a cylinder liner according to an optional embodiment of the present application.
  • FIG. 14 shows a structural schematic diagram of the cylinder liner in FIG. 13 from another perspective.
  • FIG. 15 shows a schematic cross-sectional structural view from the F-F perspective in FIG. 14 .
  • Figure 16 shows a schematic structural diagram of an upper flange according to an optional embodiment of the present application.
  • FIG. 17 shows a schematic structural view of the upper flange in FIG. 16 from a bottom perspective.
  • Figure 18 shows a schematic diagram of the internal structure of a compressor according to Embodiment 2 of the present application.
  • Fig. 19 shows a schematic structural diagram of the lower flange suction of the pump body assembly of the compressor in Fig. 18.
  • Figure 20 shows a schematic structural diagram of a cylinder liner according to an optional embodiment of the present application.
  • FIG. 21 shows a schematic structural diagram of the cylinder liner in FIG. 20 from a bottom perspective.
  • FIG. 22 shows a schematic structural diagram of the cylinder liner in FIG. 21 from another perspective.
  • Figure 23 shows a schematic structural diagram of the G-G perspective in Figure 22.
  • Figure 24 shows a schematic structural diagram of a lower flange according to an optional embodiment of the present application.
  • FIG. 25 shows a schematic structural view of the lower flange in FIG. 24 from a bottom perspective.
  • Figure 26 shows a schematic diagram of the internal structure of a compressor according to Embodiment 3 of the present application.
  • Fig. 27 shows a schematic structural diagram of the upper flange and lower suction flange of the pump body assembly of the compressor in Fig. 26.
  • Figure 28 shows a schematic structural diagram of a cylinder liner according to an optional embodiment of the present application.
  • FIG. 29 shows a schematic structural diagram of the cylinder liner in FIG. 28 from a bottom perspective.
  • FIG. 30 shows a schematic structural diagram of the cylinder liner in FIG. 28 from another perspective.
  • FIG. 31 shows a schematic cross-sectional structural view from the H-H perspective in FIG. 30 .
  • Figure 32 shows a schematic structural diagram of the exhaust of the pump body assembly according to an optional embodiment of the present application.
  • Figure 33 shows a schematic structural view of the upper flange and the lower flange of the pump body assembly in Figure 32.
  • Fig. 34 shows a schematic structural view of the cylinder liner of the pump body assembly in Fig. 32.
  • Figure 35 shows a schematic structural diagram of the exhaust of the pump body assembly according to another optional embodiment of the present application.
  • Figure 36 shows a schematic structural view of the upper flange of the pump body assembly in Figure 35.
  • Fig. 37 shows a schematic structural diagram of the cylinder liner in Fig. 35.
  • Figure 38 shows a schematic diagram of the mechanism of compressor operation according to an optional embodiment of the present application.
  • Fig. 39 shows a schematic diagram of the mechanism of the operation of the compressor in Fig. 38.
  • Figure 40 shows a schematic diagram of the mechanism of compressor operation in the related art.
  • Figure 41 shows a schematic diagram of the mechanism of the improved compressor operation in the related art.
  • Figure 42 shows a schematic diagram of the mechanism of the operation of the compressor in Figure 41. In this figure, the force arm of the drive shaft driving the slider to rotate is shown.
  • Figure 43 shows a schematic diagram of the mechanism of the operation of the compressor in Figure 41.
  • the center of the limiting groove structure coincides with the center of the eccentric portion.
  • Figure 44 shows the influence of the ratio of the cross-sectional area S of the hole cross section of the radial suction hole to the displacement V of the fluid machine on the volumetric efficiency of the compressor.
  • 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 body 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 body of the drive shaft.
  • 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 machine and heat exchange equipment, wherein the heat exchange equipment includes the above-mentioned and following fluid machines.
  • 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 In the two through holes 41 of the two sliders 40, the two sliders 40 are slidably arranged in the two limiting channels 31 and form a variable volume cavity 311.
  • the variable volume cavity 311 is located in the sliding direction of the slider 40.
  • the crankshaft 10 rotates to drive the slider 40 to slide back and forth in the limiting channel 31 and interact with the cross groove structure 30 so that the cross groove structure 30 and the slider 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 311. Since the first included angle A between the two eccentric parts 11 is the extension direction of the two limiting channels 31 twice the second included angle B, so that 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.
  • the driving torque of the other eccentric part 11 of the two eccentric parts 11 drives the corresponding slider 40 to the maximum value, ensuring the maximum driving rotation.
  • 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 center position to continue to rotate through the cross groove structure 30, thus realizing
  • the stable operation of the fluid machinery avoids the dead center position of the movement mechanism, improves the movement reliability of the fluid machinery, and thereby 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.
  • the 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 38 ).
  • 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 O 0 O 1
  • connection between the first connecting rod L 1 and the connection 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
  • the 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.
  • this application provides a fluid machine.
  • 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 7
  • 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 portion 12 of the crankshaft 10 is integrally formed, and the shaft portion 12 has only one axis. 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 . In this way, during the process of assembling 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 chamber 311.
  • 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 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.
  • 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.
  • variable volume chamber 311 the closed space surrounded by the slider 40, the limiting channel 31, the cylinder liner 20 and the upper flange 52 (or lower flange 53) is the variable volume chamber 311.
  • the pump body assembly 83 has a total of four Variable volume chamber 311, when the crankshaft 10 rotates, the crankshaft 10 rotates 2 times, and a single variable volume chamber 311 completes one suction and exhaust process. For the compressor, the crankshaft 10 rotates 2 times, completing 4 suction and exhaust times in total. Qi process.
  • the 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 ) is the variable volume chamber 311 .
  • 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.
  • the fluid machine also includes two flanges 50.
  • the two flanges 50 are respectively provided at both axial ends of the cylinder liner 20. At least one of the two flanges 50 has an inlet structure.
  • Air channel 54 the air inlet channel 54 is used to communicate with the variable volume chamber 311, the air inlet channel 54 includes a radial suction hole 541 and an axial suction hole 542 that are connected in sequence, wherein the radial suction hole 541 has a
  • the ratio S/V of the cross-sectional area S to the displacement V of the fluid machine ranges from 0.006 to 0.01.
  • the air inlet channel 54 on the flange 50 By arranging the air inlet channel 54 on the flange 50 to include a structural form including a radial suction hole 541 and an axial suction hole 542 that are connected in sequence, at the same time, the hole cross-section of the radial suction hole 541 is reasonably optimized.
  • the ratio S/V of the area S to the displacement V of the fluid machine is in the range of 0.006 to 0.01. In this way, the suction loss of the compressor due to insufficient suction is avoided, thereby ensuring that the volumetric efficiency of the compressor can reach its maximum within this range. excellent.
  • the inner wall surface of the cylinder liner 20 has a suction chamber 23 , and the intake passage 54 communicates with the variable volume chamber 311 through the suction chamber 23 .
  • the suction chamber 23 can store a large amount of gas, so that the variable volume chamber 311 can be filled with suction air, so that the compressor can suction a sufficient amount of air, and when the suction air is insufficient, the stored gas can be supplied in time.
  • a variable volume chamber 311 is provided to ensure the compression efficiency of the compressor.
  • 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.
  • FIG. 9 to 17 there are two suction chambers 23, and the two suction chambers 23 are spaced apart along the axial direction of the cylinder liner 20.
  • the cylinder The sleeve 20 also has a suction communication cavity 24. Both suction cavities 23 are connected with the suction communication cavity 24.
  • the air inlet channel 54 is connected with the suction cavity 23 through the suction communication cavity 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 chamber 24 extends a second preset distance along the axial direction of the cylinder liner 20 , and the suction communication chamber 24 penetrates the cylinder liner 20 toward one end of the flange 50 having the air inlet passage 54 . Axial end face. 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 upper flange 52 of the two flanges 50 has an air inlet channel 54 .
  • the difference between this embodiment and the first embodiment is that, as shown in FIGS. 18 to 25 , the lower flange 53 of the two flanges 50 has an air inlet channel 54 .
  • the suction communication cavity 24 extends a third preset distance along the axial direction of the cylinder liner 20 , and one end of the suction communication cavity 24 facing the flange 50 on the corresponding side 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 there are two suction chambers 23 , and 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 cavity 24, the two suction cavities 23 are both connected to the suction communication cavity 24, and the intake passage 54 is connected to the suction cavity 23 through the suction communication cavity 24.
  • the suction communication cavity 24 extends a fourth preset distance along the axial direction of the cylinder liner 20 , and the two ends of the suction communication cavity 24 respectively penetrate the two axial end surfaces 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.
  • exhaust channels 51 are provided on the end surfaces of the two flanges 50 , and the two exhaust channels 51 are respectively connected with the variable volume chambers 311 on the corresponding side.
  • the upper and lower exhaust through the flange 50 replaces the related cylinder liner side exhaust. Since the side wall surface of the cylinder liner 20 is a curved surface, it is avoided that the exhaust passage 51 is opened on the curved cylinder liner 20, causing both sides to The two exhaust channels 51 are respectively opened on the planes of the upper flange 52 and the lower flange 53, which reduces the difficulty of processing and manufacturing the exhaust channels 51.
  • the end of the air intake passage 54 is a compression air inlet
  • the initial end of the exhaust passage 51 is a compression exhaust port.
  • the compressor switches the positions of the compression inlet and compression exhaust ports and can be used as an expander. That is, the compression exhaust port is used as the expander suction port, high-pressure gas is introduced, other pushing mechanisms rotate, and the gas is discharged through the compression inlet (expander exhaust port) after expansion.
  • the end of the air intake channel 54 is an expansion exhaust port
  • the initial end of the exhaust channel 51 is an expansion air inlet.
  • an exhaust chamber 25 is provided on the outer wall of the cylinder liner 20.
  • the cylinder liner 20 also has an exhaust port 22.
  • the exhaust port 22 is connected to the exhaust chamber 25 from the inner wall of the cylinder liner 20.
  • the fluid machine also includes an exhaust valve assembly, which is disposed in the exhaust chamber 25 and corresponding to the exhaust port 22 . In this way, the exhaust chamber 25 is used to accommodate the exhaust valve assembly, which effectively reduces the space occupied by the exhaust valve assembly, enables reasonable arrangement of components, and improves the space utilization of the cylinder liner 20 .
  • the exhaust valve assembly is connected to the cylinder liner 20 through fasteners.
  • the exhaust valve assembly includes an exhaust valve plate and a valve plate baffle.
  • the exhaust valve plate is arranged in the exhaust chamber 25 and blocks the corresponding compressed exhaust gas.
  • Port 22, the valve plate baffle is overlapped and arranged on the exhaust valve plate. In this way, the arrangement of the valve plate baffle effectively prevents the exhaust valve plate from excessively opening, thereby ensuring the exhaust performance of the cylinder liner 20 .
  • the fasteners are screws.
  • a communication hole 26 is also provided on at least one axial end surface of the cylinder liner 20 .
  • the communication hole 26 is connected to the exhaust chamber 25 , and the two methods are
  • the flange 50 of the flange 50 opposite to the communication hole 26 is provided with an exhaust channel 51, and the communication hole 26 is connected with the exhaust channel 51. In this way, the exhaust reliability of the cylinder liner 20 is ensured.
  • the two exhaust chambers 25 are connected through the exhaust communication port 28, and a communication hole 26 is also provided on at least one axial end surface of the cylinder liner 20.
  • the communication hole 26 is connected with the exhaust chamber 25.
  • the flange 50 opposite to the communication hole 26 is provided with an exhaust channel 51 , and the communication hole 26 is connected with the exhaust channel 51 . In this way, the exhaust from the cylinder liner 20 side is then transferred to the exhaust passage 51 of the upper flange 52 for exhaust.
  • the two exhaust chambers 25 are not connected, and communication holes 26 are provided on both axial end surfaces of the cylinder liner 20.
  • the two communication holes 26 are connected to the two rows respectively.
  • the air chambers 25 are connected, and exhaust channels 51 are provided at the positions of the two flanges 50 that are opposite to the communication holes 26 .
  • the communication holes 26 are connected with the exhaust channels 51 .
  • the exhaust port 22 is connected with the variable volume chamber 311 on the corresponding side.
  • At least one axial end surface of the cylinder liner 20 is also provided with a communication hole 26.
  • the communication hole 26 is connected with the exhaust chamber 25.
  • the flange 50 opposite to the communication hole 26 is provided with a first exhaust channel 511.
  • the communication hole 26 is connected with the first exhaust channel 511; the two flanges 50
  • the flange 50 on the side away from the exhaust port 22 has a second exhaust channel 512 , and the second exhaust channel 512 is connected with the variable volume chamber 311 on the corresponding side. In this way, side exhaust of the cylinder liner 20 is achieved combined with end exhaust of the flange 50 .
  • the exhaust chamber 25 penetrates to the outer wall surface of the cylinder liner 20.
  • the fluid machine also includes an exhaust cover plate 70.
  • the exhaust cover plate 70 is connected to the cylinder liner 20 and seals the exhaust chamber 25. In this way, the exhaust cover 70 serves to separate the variable volume chamber 311 from the external space of the pump body assembly 83 .
  • an oblique cutout 27 is formed in the inner circle of the end of the cylinder liner 20 away from the exhaust port 22 , and the oblique cutout 27 is connected with the second exhaust passage 512 .
  • the end of the intake passage 54 is a compression intake port
  • the exhaust port 22 on the cylinder liner 20 is a compression exhaust port.
  • the compression intake port is in contact with the corresponding side.
  • the variable volume chamber 311 of the sliding block 40 is in the exhaust position, and the variable volume chamber 311 of the corresponding side is connected to the compression exhaust port.
  • the compressor switches the positions of the suction and exhaust ports and can be used as an expander. That is, the compression exhaust port of the compressor is used as the expander suction port, high-pressure gas is introduced, other pushing mechanisms rotate, and the gas is discharged through the compression inlet (expander exhaust port) after expansion.
  • the end of the intake passage 54 is the expansion exhaust port 22, and the exhaust port 22 on the cylinder liner 20 is the expansion intake port.
  • the expansion exhaust port 22 and The variable volume chamber 311 on the corresponding side is in communication; when any slider 40 is in the exhaust position, the variable volume chamber 311 on the corresponding side is in communication with the expansion air inlet.
  • the crankshaft 10 can be made to output power.
  • the inner wall surface of the cylinder liner 20 has an expansion exhaust chamber, and the expansion exhaust chamber is connected with the expansion exhaust port.
  • the expansion exhaust chamber extends a first preset distance around the circumference of the inner wall surface of the cylinder liner 20 to form an arc-shaped expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the expansion air inlet.
  • One side extends, and the extension direction of the expansion exhaust chamber is in the same direction as the rotation direction of the cross groove structure 30 .
  • the cylinder liner 20 also has an expansion exhaust communication chamber, and both expansion exhaust chambers are connected with the expansion exhaust.
  • the expansion exhaust port is connected with the expansion exhaust chamber through the expansion exhaust connecting chamber.
  • the expansion exhaust communication chamber extends along the axial direction of the cylinder liner 20 for a second preset distance, and at least one end of the expansion exhaust communication chamber penetrates the axial end surface of the cylinder liner 20 .
  • 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)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

一种流体机械和换热设备。流体机械包括曲轴（10）、缸套（20）、交叉槽结构（30）、滑块（40）和两个法兰（50），曲轴（10）有两个偏心部（11）；曲轴（10）与缸套（20）偏心且偏心距离固定；交叉槽结构（30）可转动地设在缸套（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，限位通道（31）垂直于曲轴（10）的轴向延伸；两个偏心部（11）对应伸入两个滑块（40）的两个通孔（41）内，两个法兰（50）的至少一个具有进气通道（54），包括顺次连通的径向吸气孔（541）和轴向吸气孔（542），径向吸气孔（541）的孔截面的截面积S与流体机械的排量V的比值S/V的范围为0.006-0.01。该流体机械能效较高，噪音较小，运行稳定。

Description

流体机械和换热设备
相关申请
本申请要求2022年05月23日申请的，申请号为202210565499.5，名称为“流体机械和换热设备”的中国专利申请的优先权，在此将其全文引入作为参考。
技术领域
本申请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
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。
根据国家节能环保政策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。
发明内容
本发明的主要目的在于提供一种流体机械和换热设备。根据本申请的一个方面，提供了一种流体机械，包括曲轴、缸套、交叉槽结构、滑块和两个法兰，曲轴沿其轴向设置有两个偏心部；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；滑块具有通孔，滑块为两个，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，曲轴转动以带动滑块在限位通道内往复滑动的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；两个法兰分别设置在缸套的轴向两端，两个法兰中的至少一个具有进气通道，进气通道用于与变容积腔连通，进气通道包括顺次连通的径向吸气孔和轴向吸气孔，其中，径向吸气孔的孔截面的截面积S与流体机械的排量V的比值S/V的范围为0.006～0.01。
可选的，缸套的内壁面具有吸气腔，进气通道通过吸气腔与变容积腔连通。
可选的，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。
可选的，吸气腔为两个，两个吸气腔沿缸套的轴向间隔设置，当两个法兰中的一个具有进气通道时，缸套还具有吸气连通腔，两个吸气腔均与吸气连通腔连通，进气通道通过吸气连通腔与吸气腔连通。
可选的，吸气连通腔沿缸套的轴向延伸第二预设距离，吸气连通腔朝向具有进气通道的法兰的一端贯通缸套的轴向端面。
可选的，吸气腔为两个，两个吸气腔沿缸套的轴向间隔设置，当两个法兰均具有进气通道时，缸套还具有两个吸气连通腔，两个吸气腔分别与两个吸气连通腔连通，两个进气通道分别通过对应侧的吸气连通腔与对应侧的吸气腔连通。
可选的，吸气连通腔沿缸套的轴向延伸第三预设距离，吸气连通腔朝向对应侧的法兰的一端贯通缸套的轴向端面。
可选的，吸气腔为两个，两个吸气腔沿缸套的轴向间隔设置，当两个法兰均具有进气通道时，缸套还具有吸气连通腔，两个吸气腔均与吸气连通腔连通，进气通道通过吸气连通腔与吸气腔连通。
可选的，吸气连通腔沿缸套的轴向延伸第四预设距离，吸气连通腔的两端分别贯通缸套的两个轴向端面。
可选的，两个法兰的端面上均开设有排气通道，两个排气通道分别与对应侧的变容积腔连通。
可选的，进气通道的末端为压缩进气口，排气通道的初始端为压缩排气口，当任一滑块处于进气位置时，压缩进气口与对应侧的变容积腔导通；当任一滑块处于排气位置时，对应侧的变容积腔与压缩排气口导通。
可选的，流体机械为压缩机。
可选的，进气通道的末端为膨胀排气口，排气通道的初始端为膨胀进气口，当任一滑块处于进气位置时，膨胀排气口与对应侧的变容积腔导通；当任一滑块处于排气位置时，对应侧的变容积腔与膨胀进气口导通。
可选的，流体机械为膨胀机。
可选的，缸套的外壁上开设有排气腔，缸套还具有排气口，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排气口设置。
可选的，排气口为两个，两个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排气口设置。
可选的，排气腔为一个，缸套的至少一个轴向端面上还设置有连通孔，连通孔与排气腔连通，两个法兰中与连通孔相对的法兰上开设有排气通道，连通孔与排气通道连通。
可选的，排气口为两个，两个排气口沿缸套的轴向间隔设置，排气腔为两个，两个排气腔与两个排气口一一对应地设置，排气阀组件为两组，两组排气阀组件分别对应两个排气口设置。
可选的，两个排气腔通过排气连通口连通，缸套的至少一个轴向端面上还设置有连通孔，连通孔与排气腔连通，两个法兰中与连通孔相对的法兰上开设有排气通道，连通孔与排气通道连通。
可选的，两个排气腔不连通，缸套的两个轴向端面上均设置有连通孔，两个连通孔分别与两个排气腔连通，两个法兰与连通孔相对的位置处均开设有排气通道，连通孔与排气通道连通。
可选的，排气口为一个，且排气口与对应侧的变容积腔连通，缸套的至少一个轴向端面上还设置有连通孔，连通孔与排气腔连通，两个法兰中与连通孔相对的法兰上开设有第一排气通道，连通孔与第一排气通道连通；两个法兰中远离排气口一侧的法兰具有第二排气通道，第二排气通道与对应侧的变容积腔连通。
可选的，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。
可选的，进气通道的末端为压缩进气口，缸套上的排气口为压缩排气口，当任一滑块处于进气位置时，压缩进气口与对应侧的变容积腔导通；当任一滑块处于排气位置时，对应侧的变容积腔与压缩排气口导通。
可选的，流体机械为压缩机。
可选的，进气通道的末端为膨胀排气口，缸套上的排气口为膨胀进气口，当任一滑块处于进气位置时，膨胀排气口与对应侧的变容积腔导通；当任一滑块处于排气位置时，对应侧的变容积腔与膨胀进气口导通。
可选的，流体机械为膨胀机。
可选的，两个偏心部之间具有第一夹角A的相位差，两个偏心部的偏心量相等，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。
根据本申请的另一方面，提供了一种换热设备，包括流体机械，流体机械为上述的流体机械。
附图说明
为了更清楚地说明本申请实施例或传统技术中的技术方案，下面将对实施例或传统技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请 的实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据公开的附图获得其他的附图。
图1示出了根据本申请的实施例一的压缩机的内部结构示意图。
图2示出了图1中的压缩机的泵体组件的分解结构示意图。
图3示出了图2中的曲轴、交叉槽结构、滑块的装配结构示意图。
图4示出了图3中的曲轴、交叉槽结构、滑块的剖视结构示意图。
图5示出了图2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6示出了图2中的曲轴和缸套的装配偏心量的剖视结构示意图。
图7示出了图2中的缸套和下法兰之间的偏心量的结构示意图。
图8示出了图2中的滑块在通孔轴向上的结构示意图。
图9示出了图1中的压缩机的泵体组件的上法兰吸气的结构示意图。
图10示出了图9中的泵体组件的上法兰吸气的吸气路径的结构示意图。
图11示出了图9中的C-C视角的剖视结构示意图。
图12示出了图9中的D-D视角的剖视结构示意图。
图13示出了根据本申请的一种可选实施例的缸套的结构示意图。
图14示出了图13中的缸套的另一个视角的结构示意图。
图15示出了图14中的F-F视角的剖视结构示意图。
图16示出了根据本申请的一种可选实施例的上法兰的结构示意图。
图17示出了图16中的上法兰的底部视角的结构示意图。
图18示出了根据本申请的实施例二的压缩机的内部结构示意图。
图19示出了图18中的压缩机的泵体组件的下法兰吸气的结构示意图。
图20示出了根据本申请的一种可选实施例的缸套的结构示意图。
图21示出了图20中的缸套的底部视角的结构示意图。
图22示出了图21中的缸套的另一个视角的结构示意图。
图23示出了图22中的G-G视角的结构示意图。
图24示出了根据本申请的一种可选实施例的下法兰的结构示意图。
图25示出了图24中的下法兰的底部视角的结构示意图。
图26示出了根据本申请的实施例三的压缩机的内部结构示意图。
图27示出了图26中的压缩机的泵体组件的上法兰和下法兰吸气的结构示意图。
图28示出了根据本申请的一种可选实施例的缸套的结构示意图。
图29示出了图28中的缸套的底部视角的结构示意图。
图30示出了图28中的缸套的另一个视角的结构示意图。
图31示出了图30中的H-H视角的剖视结构示意图。
图32示出了根据本申请的一种可选实施例的泵体组件的排气的结构示意图。
图33示出了图32中的泵体组件的上法兰和下法兰的结构示意图。
图34示出了图32中的泵体组件的缸套的结构示意图。
图35示出了根据本申请的另一种可选实施例的泵体组件的排气的结构示意图。
图36示出了图35中的泵体组件的上法兰的结构示意图。
图37示出了图35中的缸套的结构示意图。
图38示出了根据本申请的一种可选实施例的压缩机运行的机构原理示意图。
图39示出了图38中的压缩机运行的机构原理示意图。
图40示出了相关技术中的压缩机运行的机构原理示意图。
图41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42示出了图41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43示出了图41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。
图44示出了径向吸气孔的孔截面的截面积S与流体机械的排量V的比值对压缩机的容积效率的影响。
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；22、排气口；23、吸气腔；24、吸气连通腔；25、排气腔；26、连通孔；27、斜切口；28、排气连通口；30、交叉槽结构；31、限位通道；311、变容积腔；32、中心孔；40、滑块；41、通孔；42、挤压面；50、法兰；51、排气通道；511、第一排气通道；512、第二排气通道；52、上法兰；53、下法兰；54、进气通道；541、径向吸气孔；542、轴向吸气孔；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。
具体实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
相关技术中，如图40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41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42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43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，本申请提出了一种全新的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全新的压缩机，该压缩机具备能效高、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流体机械。
为了解决相关技术中的压缩机的能效较低、噪音较大的问题，本申请提供了一种流体机械和换热设备，其中，换热设备包括上述和下述的流体机械。
本申请实施例中的流体机械包括曲轴10、缸套20、交叉槽结构30和滑块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，两 个偏心部11的偏心量相等；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，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，由于本申请实施例提供的流体机械能够稳定运行，即，确保了压缩机的能效较高、噪音较小，从而确保换热设备的工作可靠性。
在本申请实施例中，第一夹角A和第二夹角B均不为零。
如图38和图39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38)。
如图38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39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。
进一步地，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。
在本申请中，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。
在本申请中，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。
为了解决相关技术中的压缩机的能效较低、噪音较大的问题，本申请提供了一种流体机械。
如图1至图37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5所示，两个偏心部11的偏心量均等于e，如图6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7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。
可选地，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。
可选地，第一装配间隙的范围为0.01～0.03mm。
可选地，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。
可选地，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为0.005mm～0.1mm。
如图1至图6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。
在本申请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。
可选地，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1至图6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。
在本申请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。
如图2和图3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。
在本申请中，第一夹角A为160度-200度；第二夹角B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。
可选地，第一夹角A为160度，第二夹角B为80度。
可选地，第一夹角A为165度，第二夹角B为82.5度。
可选地，第一夹角A为170度，第二夹角B为85度。
可选地，第一夹角A为175度，第二夹角B为87.5度。
可选地，第一夹角A为180度，第二夹角B为90度。
可选地，第一夹角A为185度，第二夹角B为92.5度。
可选地，第一夹角A为190度，第二夹角B为95度。
可选地，第一夹角A为195度，第二夹角B为97.5度。
在本申请中，偏心部11具有圆弧面，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1至图6所示，偏心部11为圆柱形。
可选地，偏心部11的近端与曲轴10的轴体部分12的外圆平齐。
可选地，偏心部11的近端突出于曲轴10的轴体部分12的外圆。
可选地，偏心部11的近端位于曲轴10的轴体部分12的外圆的内侧。
在本申请一个未图示的实施例中，滑块40包括多个子结构，多个子结构拼接后围成通孔41。
如图1至图6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2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12的直径。这样，确保曲轴10能够顺利地穿过中心孔32。
可选地，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，滑块40具有与第一滑移面配合的第二滑移面，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8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8中的X虚线表示两个弧面的弧心所在的圆。
可选地，弧面的曲率半径与缸套20的内圆的半径相等。
可选地，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。
可选地，差值的范围为-0.02～0.02mm。
在本申请中，挤压面42在滑块40滑动方向上的投影面积S 滑块与缸套20的压缩排气口22的面积S 排之间满足：S 滑块/S 排的值为8～25。
可选地，S 滑块/S 排的值为12～18。
本实施例示出的流体机械为压缩机，如图1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。
可选地，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2和图3。
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。
进一步地，滑块40的头部的挤压面42、限位通道31的两个侧壁面和通道底面、缸套20的部分内壁面、上法兰52的朝向缸套20一侧的部分表面(或下法兰53朝向缸套20一侧的部分表面)围成的封闭空间即为变容积腔311。
下面对压缩机的运行进行具体介绍：
如图1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。
针对如何解决压缩机吸气不足的问题，本申请在上述流体机械的基础上补充了以下内容，具体如下：
实施例一
如图9至图17、图44所示，流体机械还包括两个法兰50，两个法兰50分别设置在缸套20的轴向两端，两个法兰50中的至少一个具有进气通道54，进气通道54用于与变容积腔311连通，进气通道54包括顺次连通的径向吸气孔541和轴向吸气孔542，其中，径向吸气孔541的孔截面的截面积S与流体机械的排量V的比值S/V的范围为0.006～0.01。
通过将法兰50上的进气通道54设置成包括顺次连通的径向吸气孔541和轴向吸气孔542的结构形式，同时，合理优化径向吸气孔541的孔截面的截面积S与流体机械的排量V的比值S/V的范围在0.006～0.01内，这样，避免压缩机因吸气不足而导致吸气损失，从而确保压缩机的容积效率在此范围能够达到最优。
如图9至图17所示，缸套20的内壁面具有吸气腔23，进气通道54通过吸气腔23与变容积腔311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。
可选地，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9至图17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，当两个法兰50中的一个具有进气通道54时，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，进气通道54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9至图17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朝向具有进气通道54的法兰50的一端贯通缸套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。
在本实施例中，两个法兰50中位于上方的上法兰52上具有进气通道54。
实施例二
本实施例与实施例一的区别在于，如图18至图25所示，两个法兰50中位于下方的下法兰53上具有进气通道54。
实施例三
如图26至图31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，当两个法兰50均具有进气通道54时，缸套20还具有两个吸气连通腔24，两个吸气腔23分别与两个吸气连通腔24连通，两个进气通道54分别通过对应侧的吸气连通腔24与对应侧的吸气腔23连通。这样，实现了上法兰52和下法兰53相互独立吸气的目的。
进一步地，吸气连通腔24沿缸套20的轴向延伸第三预设距离，吸气连通腔24朝向对应侧的法兰50的一端贯通缸套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。
在本申请的一个未图示的实施例中，吸气腔23为两个，两个吸气腔23沿缸套20的轴向间隔设置，当两个法兰50均具有进气通道54时，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，进气通道54通过吸气连通腔24与吸气腔23连通。
进一步地，吸气连通腔24沿缸套20的轴向延伸第四预设距离，吸气连通腔24的两端分别贯通缸套20的两个轴向端面。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。
排气实施例一，上法兰52和下法兰53分别进行排气，具体如下：
在本申请的一个未图示的实施例中，两个法兰50的端面上均开设有排气通道51，两个排气通道51分别与对应侧的变容积腔311连通。这样，通过法兰50的上下排气代替了相关的缸套侧排气，由于缸套20的侧壁面为弧面，避免排气通道51开设在呈弧面的缸套20上，而使得两个排气通道51分别开设在上法兰52和下法兰53的平面上，降低了排气通道51的加工制造难度。
具体而言，进气通道54的末端为压缩进气口，排气通道51的初始端为压缩排气口，当任一滑块40处于进气位置时，压缩进气口与对应侧的变容积腔311导通；当任一滑块40处于排气位置时，对应侧的变容积腔311与压缩排气口导通。这样，当高压气体通过压缩进气口进入变容积腔311内后，高压气体推动交叉槽结构30旋转，交叉槽结构30旋转以带动滑块40旋转，并同时使滑块40相对于交叉槽结构30直线滑动，进而使得滑块40带动偏心部11旋转，即，带动曲轴10转动。通过将该曲轴10与其他耗功设备连接，可以使曲轴10输出做功。
其他使用场合：该压缩机将压缩进气口、压缩排气口交换位置，可以作为膨胀机使用。即，将压缩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，膨胀后通过压缩进气口(膨胀机排气口)排出气体。
具体而言，进气通道54的末端为膨胀排气口，排气通道51的初始端为膨胀进气口，当任一滑块40处于进气位置时，膨胀排气口与对应侧的变容积腔311导通；当任一滑块40处于排气位置时，对应侧的变容积腔311与膨胀进气口导通。这样，当高压气体通过膨胀进气口进入变容积腔311内后，高压气体推动交叉槽结构30旋转，交叉槽结构30旋转以带动滑块40旋转，并同时使滑块40相对于交叉槽结构30直线滑动，进而使得滑块40带动偏心部11旋转，即，带动曲轴10转动。通过将该曲轴10与其他耗功设备连接，可以使曲轴10输出做功。
排气实施例二，缸套侧排气，具体如下：
如图32至图34所示，缸套20的外壁上开设有排气腔25，缸套20还具有排气口22，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，排气阀组件设置在排气腔25内并对应排气口22设置。这样，排气腔25用于容纳排气阀组件，有效减少了排气阀组件的占用空间，使得部件合理布置，提高了缸套20的空间利用率。
如图32至图34所示，排气口22为两个，两个排气口22沿缸套20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，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。
进一步地，排气阀组件通过紧固件与缸套20连接，排气阀组件包括排气阀片和阀片挡板，排气阀片设置在排气腔25内并遮挡对应的压缩排气口22，阀片挡板重叠设置在排气阀片上。这样，阀片挡板的设置，有效避免了排气阀片过渡开启，从而保证了缸套20的排气性能。
可选地，紧固件为螺钉。
在本申请的一个未图示的实施例中，排气腔25为一个，缸套20的至少一个轴向端面上还设置有连通孔26，连通孔26与排气腔25连通，两个法兰50中与连通孔26相对的法兰50上开设有排气通道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32至图34所示，排气口22为两个，两个排气口22沿缸套20的轴向间隔设置，排气腔25为两个，两个排气腔25与两个排气口22一一对应地设置，排气阀组件为两组，两组排气阀组件分别对应两个排气口22设置。
如图32至图34所示，两个排气腔25通过排气连通口28连通，缸套20的至少一个轴向端面上还设置有连通孔26，连通孔26与排气腔25连通，两个法兰50中与连通孔26相对的法兰50上开设有排气通道51，连通孔26与排气通道51连通。这样，缸套20侧排气后再转为上法兰52的排气通道51进行排气。
在本申请的另一个未图示的实施例中，两个排气腔25不连通，缸套20的两个轴向端面上均设置有连通孔26，两个连通孔26分别与两个排气腔25连通，两个法兰50与连通孔26相对的位置处均开设有排气通道51，连通孔26与排气通道51连通。这样，缸套20的上下部分分别进行侧排气，再分别转为上法兰52的上排气，以及转为下法兰53的下排气。
排气实施例三，缸套侧排气和法兰的端面排气，具体如下：
如图35至图37所示，排气口22为一个，且排气口22与对应侧的变容积腔311连通，缸套20的至少一个轴向端面上还设置有连通孔26，连通孔26与排气腔25连通，两个法兰50中与连通孔26相对的法兰50上开设有第一排气通道511，连通孔26与第一排气通道511连通；两个法兰50中远离排气口22一侧的法兰50具有第二排气通道512，第二排气通道512与对应侧的变容积腔311连通。这样，实现缸套20的侧排气并结合了法兰50的端部排气。
如图35至图37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。
如图37所示，缸套20远离排气口22一侧的端部内圆处开设有斜切口27，且斜切口27与第二排气通道512连通。
具体而言，进气通道54的末端为压缩进气口，缸套20上的排气口22为压缩排气口，当任一滑块40处于进气位置时，压缩进气口与对应侧的变容积腔311导通；当任一滑块40处于排气位置时，对应侧的变容积腔311与压缩排气口导通。这样，当高压气体通过压缩进气口进入变容积腔311内后，高压气体推动交叉槽结构30旋转，交叉槽结构30旋转 以带动滑块40旋转，并同时使滑块40相对于交叉槽结构30直线滑动，进而使得滑块40带动偏心部11旋转，即，带动曲轴10转动。通过将该曲轴10与其他耗功设备连接，可以使曲轴10输出做功。
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，将压缩机的压缩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，膨胀后通过压缩进气口(膨胀机排气口)排出气体。
具体而言，进气通道54的末端为膨胀排气口22，缸套20上的排气口22为膨胀进气口，当任一滑块40处于进气位置时，膨胀排气口22与对应侧的变容积腔311导通；当任一滑块40处于排气位置时，对应侧的变容积腔311与膨胀进气口导通。这样，当高压气体通过膨胀进气口进入变容积腔311内后，高压气体推动交叉槽结构30旋转，交叉槽结构30旋转以带动滑块40旋转，并同时使滑块40相对于交叉槽结构30直线滑动，进而使得滑块40带动偏心部11旋转，即，带动曲轴10转动。通过将该曲轴10与其他耗功设备连接，可以使曲轴10输出做功。
可选地，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。
进一步地，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。
进一步地，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。
进一步地，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。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、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申请的范围。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申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、工作、器件、组件和/或它们的组合。
本申请的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本申请的实施方式能够以除了在这里图示或描述的那些以外的顺序实施。
以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上所述实施例仅表达了本申请的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对申请专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请专利的保护范围应以所附权利要求为准。

Claims (28)

  1. 一种流体机械，其特征在于，包括：
    曲轴(10)，所述曲轴(10)沿其轴向设置有两个偏心部(11)；
    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；
    滑块(40)，所述滑块(40)具有通孔(41)，所述滑块(40)为两个，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)转动以带动所述滑块(40)在所述限位通道(31)内往复滑动的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；
    两个法兰(50)，两个所述法兰(50)分别设置在所述缸套(20)的轴向两端，两个所述法兰(50)中的至少一个具有进气通道(54)，所述进气通道(54)用于与所述变容积腔(311)连通，所述进气通道(54)包括顺次连通的径向吸气孔(541)和轴向吸气孔(542)，其中，所述径向吸气孔(541)的孔截面的截面积S与所述流体机械的排量V的比值S/V的范围为0.006～0.01。
  2. 根据权利要求1所述的流体机械，其特征在于，所述缸套(20)的内壁面具有吸气腔(23)，所述进气通道(54)通过所述吸气腔(23)与所述变容积腔(311)连通。
  3. 根据权利要求2所述的流体机械，其特征在于，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)。
  4. 根据权利要求2所述的流体机械，其特征在于，所述吸气腔(23)为两个，两个所述吸气腔(23)沿所述缸套(20)的轴向间隔设置，当两个所述法兰(50)中的一个具有所述进气通道(54)时，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，所述进气通道(54)通过所述吸气连通腔(24)与所述吸气腔(23)连通。
  5. 根据权利要求4所述的流体机械，其特征在于，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)朝向具有所述进气通道(54)的所述法兰(50)的一端贯通所述缸套(20)的轴向端面。
  6. 根据权利要求2所述的流体机械，其特征在于，所述吸气腔(23)为两个，两个所述吸气腔(23)沿所述缸套(20)的轴向间隔设置，当两个所述法兰(50)均具有所述进气通道(54)时，所述缸套(20)还具有两个吸气连通腔(24)，两个所述吸气腔(23)分别与两个所述吸气连通腔(24)连通，两个所述进气通道(54)分别通过对应侧的所述吸气连通腔(24)与对应侧的所述吸气腔(23)连通。
  7. 根据权利要求6所述的流体机械，其特征在于，所述吸气连通腔(24)沿所述缸套(20)的轴向延伸第三预设距离，所述吸气连通腔(24)朝向对应侧的所述法兰(50)的一端贯通所述缸套(20)的轴向端面。
  8. 根据权利要求2所述的流体机械，其特征在于，所述吸气腔(23)为两个，两个所述吸气腔(23)沿所述缸套(20)的轴向间隔设置，当两个所述法兰(50)均具有所述进气通道(54)时，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，所述进气通道(54)通过所述吸气连通腔(24)与所述吸气腔(23)连通。
  9. 根据权利要求8所述的流体机械，其特征在于，所述吸气连通腔(24)沿所述缸套(20)的轴向延伸第四预设距离，所述吸气连通腔(24)的两端分别贯通所述缸套(20) 的两个轴向端面。
  10. 根据权利要求1所述的流体机械，其特征在于，两个所述法兰(50)的端面上均开设有排气通道(51)，两个所述排气通道(51)分别与对应侧的所述变容积腔(311)连通。
  11. 根据权利要求10所述的流体机械，其特征在于，所述进气通道(54)的末端为压缩进气口，所述排气通道(51)的初始端为压缩排气口，
    当任一所述滑块(40)处于进气位置时，所述压缩进气口与对应侧的所述变容积腔(311)导通；
    当任一所述滑块(40)处于排气位置时，对应侧的所述变容积腔(311)与所述压缩排气口导通。
  12. 根据权利要求11所述的流体机械，其特征在于，所述流体机械为压缩机。
  13. 根据权利要求10所述的流体机械，其特征在于，所述进气通道(54)的末端为膨胀排气口，所述排气通道(51)的初始端为膨胀进气口，
    当任一所述滑块(40)处于进气位置时，所述膨胀排气口与对应侧的所述变容积腔(311)导通；
    当任一所述滑块(40)处于排气位置时，对应侧的所述变容积腔(311)与所述膨胀进气口导通。
  14. 根据权利要求13所述的流体机械，其特征在于，所述流体机械为膨胀机。
  15. 根据权利要求1所述的流体机械，其特征在于，所述缸套(20)的外壁上开设有排气腔(25)，所述缸套(20)还具有排气口(22)，所述排气口(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，所述排气阀组件设置在所述排气腔(25)内并对应所述排气口(22)设置。
  16. 根据权利要求15所述的流体机械，其特征在于，所述排气口(22)为两个，两个所述排气口(22)沿所述缸套(20)的轴向间隔设置，所述排气阀组件为两组，两组所述排气阀组件分别对应两个所述排气口(22)设置。
  17. 根据权利要求16所述的流体机械，其特征在于，所述排气腔(25)为一个，所述缸套(20)的至少一个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，两个所述法兰(50)中与所述连通孔(26)相对的所述法兰(50)上开设有排气通道(51)，所述连通孔(26)与所述排气通道(51)连通。
  18. 根据权利要求15所述的流体机械，其特征在于，所述排气口(22)为两个，两个所述排气口(22)沿所述缸套(20)的轴向间隔设置，所述排气腔(25)为两个，两个所述排气腔(25)与两个所述排气口(22)一一对应地设置，所述排气阀组件为两组，两组所述排气阀组件分别对应两个所述排气口(22)设置。
  19. 根据权利要求18所述的流体机械，其特征在于，两个所述排气腔(25)通过排气连通口(28)连通，所述缸套(20)的至少一个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，两个所述法兰(50)中与所述连通孔(26)相对的所述法兰(50)上开设有排气通道(51)，所述连通孔(26)与所述排气通道(51)连通。
  20. 根据权利要求18所述的流体机械，其特征在于，两个所述排气腔(25)不连通，所述缸套(20)的两个轴向端面上均设置有连通孔(26)，两个所述连通孔(26)分别与两个所述排气腔(25)连通，两个所述法兰(50)与所述连通孔(26)相对的位置处均开设有排气通道(51)，所述连通孔(26)与所述排气通道(51)连通。
  21. 根据权利要求15所述的流体机械，其特征在于，所述排气口(22)为一个，且所述排气口(22)与对应侧的所述变容积腔(311)连通，所述缸套(20)的至少一个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，两个所述法兰(50)中与所述连通孔(26)相对的所述法兰(50)上开设有第一排气通道(511)，所述 连通孔(26)与所述第一排气通道(511)连通；两个所述法兰(50)中远离所述排气口(22)一侧的所述法兰(50)具有第二排气通道(512)，所述第二排气通道(512)与对应侧的所述变容积腔(311)连通。
  22. 根据权利要求15所述的流体机械，其特征在于，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)。
  23. 根据权利要求15至22中任一项所述的流体机械，其特征在于，所述进气通道(54)的末端为压缩进气口，所述缸套(20)上的所述排气口(22)为压缩排气口，
    当任一所述滑块(40)处于进气位置时，所述压缩进气口与对应侧的所述变容积腔(311)导通；
    当任一所述滑块(40)处于排气位置时，对应侧的所述变容积腔(311)与所述压缩排气口导通。
  24. 根据权利要求23所述的流体机械，其特征在于，所述流体机械为压缩机。
  25. 根据权利要求15至22中任一项所述的流体机械，其特征在于，所述进气通道(54)的末端为膨胀排气口(22)，所述缸套(20)上的排气口(22)为膨胀进气口，
    当任一所述滑块(40)处于进气位置时，所述膨胀排气口(22)与对应侧的所述变容积腔(311)导通；
    当任一所述滑块(40)处于排气位置时，对应侧的所述变容积腔(311)与所述膨胀进气口导通。
  26. 根据权利要求25所述的流体机械，其特征在于，所述流体机械为膨胀机。
  27. 根据权利要求1所述的流体机械，其特征在于，两个所述偏心部(11)之间具有第一夹角(A)的相位差，两个所述偏心部(11)的偏心量相等，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。
  28. 一种换热设备，包括流体机械，其特征在于，所述流体机械为权利要求1至27中任一项所述的流体机械。
PCT/CN2022/140975 2022-05-23 2022-12-22 流体机械和换热设备 WO2023226411A1 (zh)

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WO2017024868A1 (zh) * 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 流体机械、换热设备和流体机械的运行方法
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JPS59155580A (ja) * 1983-02-25 1984-09-04 Hitachi Ltd 容量制御型圧縮機
US20130133511A1 (en) * 2010-08-02 2013-05-30 Yugen Kaisha K. R & D Fluid rotary machine
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