Fluid machinery, heat exchange equipment, and operating methods of fluid machinery.

Abstract

This invention provides a fluid machine, a heat exchanger, and a method for operating the fluid machine. The fluid machine includes a crankshaft, a cylinder liner, a cross-groove structure, and sliders. The crankshaft has a first included angle A between its two eccentric portions. The crankshaft and cylinder liner are eccentrically positioned with a fixed eccentricity. The first and second cross-groove sections of the cross-groove structure are coaxially arranged and movably connected. Both the first and second cross-groove sections have limiting channels, which are sequentially arranged along the axial direction of the crankshaft. The extending direction of the limiting channels is perpendicular to the axial direction of the crankshaft, and a second included angle B is formed between the extending directions of the two limiting channels. The first included angle A is twice the second included angle B. The two eccentric portions extend into the two through holes of the two sliders, which are slidably positioned within the two limiting channels, forming a variable volume cavity. This invention solves the problems of low energy efficiency and high noise in existing compressors.

Description

Technical Field

[0001] This invention relates to the field of heat exchange system technology, and more specifically, to a fluid machine, a heat exchange device, and a method for operating the fluid machine. Background Technology

[0002] Fluid machinery in the prior art includes compressors and expanders, among others. Let's take compressors as an example.

[0003] In accordance with national energy conservation and environmental protection policies and consumer demands for air conditioning comfort, the air conditioning industry has been pursuing high efficiency and low noise. The compressor, as the heart of the air conditioner, directly impacts its energy efficiency and noise level. Scroll compressors, as the mainstream type of household air conditioner compressor, have matured after nearly a century of development, but their structural principles limit their potential for optimization. Significant breakthroughs require innovation in their structural principles.

[0004] Therefore, there is an urgent need to develop a compressor with high energy efficiency and low noise. Summary of the Invention

[0005] The main objective of this invention is to provide a fluid machine, a heat exchange device, and a method for operating the fluid machine, so as to solve the problems of low energy efficiency and high noise in the compressor in the prior art.

[0006] To achieve the above objectives, according to one aspect of the present invention, a fluid machine is provided, comprising a crankshaft, a cylinder liner, a cross-groove structure, and a slider, wherein the crankshaft has two eccentric portions arranged along its axial direction, and the two eccentric portions have a phase difference of a first included angle A; the crankshaft and the cylinder liner are eccentrically arranged with a fixed eccentric distance; the cross-groove structure is rotatably disposed within the cylinder liner, and the cross-groove structure includes a first cross-groove segment and a second cross-groove segment connected along its axial direction, the first cross-groove segment and the second cross-groove segment being coaxially arranged and movably connected, and both the first cross-groove segment and the second cross-groove segment having a limiting channel, the two limiting channels... The limiting channels are sequentially arranged along the crankshaft axis. The extension direction of the limiting channels is perpendicular to the crankshaft axis, and there is a phase difference of a second included angle B between the extension directions of the two limiting channels. The first included angle A is twice the second included angle B. The slider has a through hole, and there are two sliders. The two eccentric parts extend into the two through holes of the two sliders respectively. The two sliders are slidably arranged in the two limiting channels and form a variable volume cavity. The variable volume cavity is located in the sliding direction of the slider. The crankshaft rotates to drive the slider to slide back and forth in the limiting channel while interacting with the cross groove structure, so that the cross groove structure and the slider rotate in the cylinder liner.

[0007] Furthermore, the distance between the inner ring axis of the cylinder liner located at the first cross groove section and the inner ring axis of the cylinder liner located at the second cross groove section is equal to the eccentric distance between the first cross groove section and the second cross groove section.

[0008] Furthermore, the cross-slot structure also includes a first sliding connector. The first cross-slot segment is movably connected to the second cross-slot segment through the first sliding connector. When the first cross-slot segment rotates, the first sliding connector slides relative to the first cross-slot segment. When the second cross-slot segment rotates, the first sliding connector slides relative to the second cross-slot segment.

[0009] Furthermore, the first sliding connector has two first limiting grooves, both of which extend perpendicularly to the crankshaft axis and are perpendicular to each other. The end of the first cross groove section facing the first sliding connector has a third protrusion, and the end of the second cross groove section facing the first sliding connector has a fourth protrusion. The third and fourth protrusions are slidably disposed within the two first limiting grooves. The first cross groove section rotates to allow the third protrusion to reciprocate within its corresponding first limiting groove while interacting with the first sliding connector. The first sliding connector rotates and drives the fourth protrusion to reciprocate within its corresponding first limiting groove, simultaneously driving the second cross groove section to rotate. Alternatively, the second cross groove section rotates to allow the fourth protrusion to reciprocate within its corresponding first limiting groove while interacting with the first sliding connector. The first sliding connector rotates and drives the third protrusion to reciprocate within its corresponding first limiting groove, simultaneously driving the first cross groove section to rotate.

[0010] Furthermore, the first sliding connector has two first limiting protrusions extending toward the first and second intersecting groove segments respectively; the end of the first intersecting groove segment facing the first sliding connector has a third sliding groove structure, and the end of the second intersecting groove segment facing the first sliding connector has a fourth sliding groove structure. The two first limiting protrusions are slidably disposed within the third and fourth sliding groove structures respectively, and the extension direction of the third sliding groove structure is perpendicular to the extension direction of the fourth sliding groove structure. When the first intersecting groove segment rotates to make the corresponding first limiting protrusion slide back and forth within the third sliding groove structure, the third sliding groove structure interacts with the first sliding connector. The first sliding connector rotates and drives the first limiting protrusion to slide back and forth within the fourth sliding groove structure while simultaneously driving the second intersecting groove segment to rotate; or, when the second intersecting groove segment rotates to make the corresponding first limiting protrusion slide back and forth within the fourth sliding groove structure, the fourth sliding groove structure interacts with the first sliding connector. The first sliding connector rotates and drives the first limiting protrusion to slide back and forth within the third sliding groove structure while simultaneously driving the first intersecting groove segment to rotate.

[0011] Furthermore, the crankshaft's shaft body is integrally formed, and the shaft body has only one axis.

[0012] Furthermore, the crankshaft shaft portion includes a first section and a second section connected along its axial direction, the first section and the second section being coaxially arranged, and two eccentric parts being respectively arranged on the first section and the second section.

[0013] Furthermore, the first and second segments are detachably connected.

[0014] Furthermore, the eccentricities of the two eccentric parts are not equal. The eccentricity of the first eccentric part is equal to the assembly eccentricity of the crankshaft and the corresponding first cross groove segment; the eccentricity of the second eccentric part is equal to the assembly eccentricity of the crankshaft and the corresponding second cross groove segment.

[0015] Furthermore, the crankshaft shaft portion includes a first section and a second section connected along its axial direction. The first section and the second section are not axially aligned but are movably connected. Two eccentric parts are respectively disposed on the first section and the second section.

[0016] Furthermore, the crankshaft also includes a sliding connector. The first section is movably connected to the second section through the sliding connector. While the first section rotates, the sliding connector slides relative to the first section, and while the second section rotates, the sliding connector slides relative to the second section.

[0017] Furthermore, the sliding connector has two limiting grooves, both extending perpendicularly to the crankshaft axis, and the extending directions of the two limiting grooves are perpendicular to each other; the end of the first segment facing the sliding connector has a first protrusion structure, and the end of the second segment facing the sliding connector has a second protrusion structure, the first protrusion structure and the second protrusion structure are respectively slidably disposed in the two limiting grooves; the first segment rotates so that the first protrusion structure reciprocates within the corresponding limiting groove while interacting with the sliding connector, and the sliding connector rotates and drives the second protrusion structure to reciprocate within the corresponding limiting groove while driving the second segment to rotate; or, the second segment rotates so that the second protrusion structure reciprocates within the corresponding limiting groove while interacting with the sliding connector, and the sliding connector rotates and drives the first protrusion structure to reciprocate within the corresponding limiting groove while driving the first segment to rotate.

[0018] Furthermore, the sliding connector has two limiting protrusions extending toward the first segment and the second segment respectively; the end of the first segment facing the sliding connector has a first groove structure, and the end of the second segment facing the sliding connector has a second groove structure. The two limiting protrusions are slidably disposed within the first groove structure and the second groove structure respectively, and the extending direction of the first groove structure is perpendicular to the extending direction of the second groove structure; while the first segment rotates to make the corresponding limiting protrusion slide back and forth within the first groove structure, the first groove structure interacts with the sliding connector, and the sliding connector rotates and drives the limiting protrusion to slide back and forth within the second groove structure while driving the second segment to rotate; or, while the second segment rotates to make the corresponding limiting protrusion slide back and forth within the second groove structure, the second groove structure interacts with the sliding connector, and the sliding connector rotates and drives the limiting protrusion to slide back and forth within the first groove structure while driving the first segment to rotate.

[0019] Furthermore, the eccentricity of the two eccentric parts is equal, wherein the assembly eccentricity of the first segment and the corresponding first cross groove segment is equal to the eccentricity of the eccentric part provided on the first segment, and the assembly eccentricity of the second segment and the corresponding second cross groove segment is equal to the eccentricity of the eccentric part provided on the second segment.

[0020] Furthermore, the eccentricity of the two eccentric parts is not equal. Specifically, the assembly eccentricity of the first segment and the corresponding first cross groove segment is equal to the eccentricity of the eccentric part set on the first segment, and the assembly eccentricity of the second cross groove segment corresponding to the second segment is equal to the eccentricity of the eccentric part set on the second segment.

[0021] Furthermore, the crankshaft shaft portion and the eccentric portion are integrally formed; or, the crankshaft shaft portion and the eccentric portion are detachably connected.

[0022] Furthermore, one of the two limiting channels extends to the outer periphery of the first intersecting groove section at both ends, and the other of the two limiting channels extends to the outer periphery of the second intersecting groove section at both ends.

[0023] Furthermore, the two sliders are respectively concentrically set with the two eccentric parts, and the sliders move in a circular motion around the axis of the crankshaft of the eccentric part. There is a first rotational gap between the hole wall and the eccentric part, and the range of the first rotational gap is 0.005mm to 0.05mm.

[0024] Furthermore, there is a second rotational clearance between the outer peripheral surface of the first cross groove section and the inner wall surface of one axial end of the cylinder liner, the second rotational clearance being in the range of 0.01mm to 0.08mm, and there is a third rotational clearance between the outer peripheral surface of the second cross groove section and the inner wall surface of the other axial end of the cylinder liner, the third rotational clearance being in the range of 0.01mm to 0.08mm.

[0025] Furthermore, the first included angle A is 160 degrees to 200 degrees; the second included angle B is 80 degrees to 100 degrees.

[0026] Furthermore, the fluid machinery also includes a flange, which is located at the axial end of the cylinder liner, and the crankshaft is concentrically positioned with the flange.

[0027] Furthermore, there is a first assembly clearance between the crankshaft and the flange, the first assembly clearance being in the range of 0.005mm to 0.05mm.

[0028] Furthermore, the range of the first assembly gap is 0.01 to 0.03 mm.

[0029] Furthermore, the eccentric part has a circular arc surface with a central angle greater than or equal to 180 degrees.

[0030] Furthermore, the eccentric part is cylindrical.

[0031] Furthermore, the proximal end of the eccentric portion is flush with the outer circle of the crankshaft body portion; or, the proximal end of the eccentric portion protrudes beyond the outer circle of the crankshaft body portion; or, the proximal end of the eccentric portion is located inside the outer circle of the crankshaft body portion.

[0032] Furthermore, the slider comprises multiple substructures, which are spliced ​​together to form a through hole.

[0033] Furthermore, the two eccentric parts are spaced apart axially on the crankshaft.

[0034] Furthermore, both the first and second cross groove sections have a central hole, the two central holes are not concentrically arranged, and the two limiting channels are connected through the two central holes. The diameter of each central hole is larger than the diameter of the crankshaft shaft portion.

[0035] Furthermore, the diameter of the central hole is larger than the diameter of the eccentric part.

[0036] Furthermore, 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.

[0037] Furthermore, the limiting channel has a set of opposing first sliding surfaces that slide in contact with the slider, the slider has a second sliding surface that cooperates with the first sliding surface, the slider has a pressing surface facing the end of the limiting channel, the pressing surface serves as the head of the slider, the two second sliding surfaces are connected through the pressing surface, and the pressing surface faces the variable volume cavity.

[0038] Furthermore, the extrusion surface is an arc surface, and the distance between the center of the arc surface and the center of the through hole is equal to the eccentricity of the eccentric part.

[0039] Furthermore, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner; or, the radius of curvature of the arc surface has a difference from the radius of the inner circle of the cylinder liner, the difference being in the range of -0.05mm to 0.025mm.

[0040] Furthermore, the difference ranges from -0.02 to 0.02 mm.

[0041] Furthermore, the projected area S of the extrusion surface in the sliding direction of the slider 滑块 The area of ​​the compression exhaust port of the cylinder liner is S 排 The following conditions must be met between them: S 滑块 / S 排 The value is 8 to 25.

[0042] Furthermore, S 滑块 / S 排 The value is 12 to 18.

[0043] Furthermore, the cylinder liner has a compression intake port and a compression exhaust port. When any slider is in the intake position, the compression intake port is connected to the corresponding variable volume chamber; when any slider is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port.

[0044] Furthermore, the inner wall of the cylinder liner has an intake chamber, which is connected to the compression intake port.

[0045] Furthermore, the intake chamber extends circumferentially around the inner wall of the cylinder liner by a first predetermined distance to form an arc-shaped intake chamber.

[0046] Furthermore, there are two intake chambers, which are spaced apart along the axial direction of the cylinder liner. The cylinder liner also has an intake connecting chamber, and both intake chambers are connected to the intake connecting chamber. The compression intake port is connected to the intake chamber through the intake connecting chamber.

[0047] Furthermore, the intake communication cavity extends a second predetermined distance along the axial direction of the cylinder liner, and at least one end of the intake communication cavity penetrates the axial end face of the cylinder liner.

[0048] Furthermore, an exhaust chamber is provided on the outer wall of the cylinder liner, and a compressed exhaust port is connected to the exhaust chamber from the inner wall of the cylinder liner. The fluid machinery also includes an exhaust valve assembly, which is disposed in the exhaust chamber and corresponding to the compressed exhaust port.

[0049] Furthermore, there are two compression exhaust ports, which are spaced apart along the axial direction of the cylinder liner. There are two sets of exhaust valve assemblies, which are respectively set to correspond to the two compression exhaust ports.

[0050] Furthermore, a connecting hole is provided on the axial end face of the cylinder liner, which communicates with the exhaust chamber. The fluid machinery also includes a flange, on which an exhaust passage is provided, and the connecting hole communicates with the exhaust passage.

[0051] Furthermore, the exhaust chamber extends to the outer wall of the cylinder liner, and the fluid machinery also includes an exhaust cover plate, which is connected to the cylinder liner and seals the exhaust chamber.

[0052] Furthermore, fluid machinery is the compressor.

[0053] Furthermore, the cylinder liner has an expansion exhaust port and an expansion intake port. When any slider is in the intake position, the expansion exhaust port is connected to the corresponding variable volume chamber; when any slider is in the exhaust position, the corresponding variable volume chamber is connected to the expansion intake port.

[0054] Furthermore, the inner wall surface of the cylinder liner has an expansion exhaust chamber, which is connected to the expansion exhaust port.

[0055] Furthermore, the expansion exhaust chamber extends circumferentially around the inner wall of the cylinder liner by a first predetermined distance to form an arc-shaped expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion intake port is located, with the extension direction of the expansion exhaust chamber being in the same direction as the rotation direction of the cross groove structure.

[0056] Furthermore, there are two expansion exhaust chambers, which are spaced apart along the axial direction of the cylinder liner. The cylinder liner also has an expansion exhaust communication chamber, and both expansion exhaust chambers are connected to the expansion exhaust communication chamber. The expansion exhaust port is connected to the expansion exhaust chamber through the expansion exhaust communication chamber.

[0057] Furthermore, the expansion exhaust communication cavity extends a second predetermined distance along the axial direction of the cylinder liner, and at least one end of the expansion exhaust communication cavity penetrates the axial end face of the cylinder liner.

[0058] Furthermore, fluid machinery is an expander.

[0059] According to another aspect of the present invention, a heat exchange device is provided, including fluid machinery, wherein the fluid machinery is the fluid machinery described above.

[0060] According to another aspect of the present invention, a method for operating fluid machinery is provided, comprising: a crankshaft rotating about its axis O0; a first cross-groove segment revolving about its axis O0, wherein the axis O0 of the crankshaft is eccentrically positioned with a fixed eccentricity to the axis O1 of the first cross-groove segment; a second cross-groove segment revolving about its axis O0, wherein the axis O0 of the crankshaft is eccentrically positioned with a fixed eccentricity to the axis O1' of the second cross-groove segment; and a first slider revolving in a circular motion about its axis O0, wherein the distance between the center O3 of the first slider and the axis O0 of the crankshaft is equal to the eccentricity of the first eccentric portion of the crankshaft, and the eccentricity is equal to the distance between the axis O0 of the crankshaft and the axis O1' of the first cross-groove segment. The eccentric distance between the axis O1 of the groove segment, the crankshaft rotates to drive the first slider to make a circular motion, and the first slider interacts with the first cross groove segment and slides back and forth in the limiting channel of the first cross groove segment; the second slider makes a circular motion with the axis O0 of the crankshaft as the center, and the distance between the center O4 of the second slider and the axis O0 of the crankshaft is equal to the eccentricity of the second eccentric part of the crankshaft, and the eccentricity is equal to the eccentric distance between the axis O0 of the crankshaft and the axis O1' of the second cross groove segment, the crankshaft rotates to drive the second slider to make a circular motion, and the second slider interacts with the second cross groove segment and slides back and forth in the limiting channel of the second cross groove segment.

[0061] Furthermore, the operating method adopts the principle of a cross-slider mechanism, wherein the two eccentric parts of the crankshaft serve as the first connecting rod L1 and the second connecting rod L2, respectively; the limiting channel of the first cross groove section serves as the third connecting rod L3; and the limiting channel of the second cross groove section serves as the fourth connecting rod L4. The lengths of the first connecting rod L1 and the second connecting rod L2 are not equal.

[0062] Furthermore, there is a first included angle A between the first link L1 and the second link L2, and a second included angle B between the third link L3 and the fourth link L4, wherein the first included angle A is twice the second included angle B.

[0063] Furthermore, the line connecting the crankshaft axis O0, the axis O1 of the first cross-groove section, and the axis O1' of the second cross-groove section is line O0O1O1'. The first connecting rod L1 has a third included angle C with line O0O1O1', and the corresponding third connecting rod L3 has a fourth included angle D with line O0O1O1', wherein the third included angle C is twice the fourth included angle D; the second connecting rod L2 has a fifth included angle E with line O0O1O1', and the corresponding fourth connecting rod L4 has a sixth included angle F with line O0O1O1', wherein the fifth included 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, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

[0064] Furthermore, the operating method also includes the slider's rotational angular velocity being the same as its revolution angular velocity; and the revolution angular velocity of the first and second intersecting slot sections being the same as the slider's rotational angular velocity.

[0065] Furthermore, during the crankshaft rotation, the crankshaft rotates 2 revolutions, completing 4 intake and exhaust processes.

[0066] Furthermore, the operating method also includes the following: the first segment of the crankshaft rotates around its axis O0, and the second segment of the crankshaft rotates around its axis O0', wherein O0 and O0' do not coincide; the axis O0 of the first segment is eccentrically set with a fixed eccentricity to the axis O1 of the first cross-groove segment, and the axis O0' of the second segment is eccentrically set with a fixed eccentricity to the axis O1' of the second cross-groove segment; the first slider moves in a circular motion around the axis O0 of the first segment, and the distance between the center O3 of the first slider and the axis O0 of the first segment is equal to the eccentricity of the eccentric portion on the first segment, and the eccentricity of the first segment is equal to the distance between the axis O0 of the first segment and the axis O1 of the first cross-groove segment. The first segment rotates to drive the first slider to make a circular motion, and the first slider interacts with the first cross groove segment and slides back and forth in the limiting channel of the first cross groove segment; the second slider makes a circular motion with the axis O0' of the second segment as the center, and the distance between the center O4 of the second slider and the axis O0' of the second segment is equal to the eccentricity of the eccentric part on the second segment, and the eccentricity of the second segment is equal to the eccentricity between the axis O0' of the second segment and the axis O1' of the second cross groove segment. The second segment rotates to drive the second slider to make a circular motion, and the second slider interacts with the second cross groove segment and slides back and forth in the limiting channel of the second cross groove segment.

[0067] Furthermore, the operating method adopts the principle of a cross-slider mechanism, wherein the eccentric part on the first segment serves as the first connecting rod L1, the eccentric part on the second segment serves as the second connecting rod L2, the limiting channel of the first cross groove segment serves as the third connecting rod L3, and the limiting channel of the second cross groove segment serves as the fourth connecting rod L4, wherein the lengths of the first connecting rod L1 and the second connecting rod L2 are equal.

[0068] Furthermore, the operating method adopts the principle of a cross-slider mechanism, wherein the eccentric part on the first segment serves as the first connecting rod L1, the eccentric part on the second segment serves as the second connecting rod L2, the limiting channel of the first cross groove segment serves as the third connecting rod L3, and the limiting channel of the second cross groove segment serves as the fourth connecting rod L4. The lengths of the first connecting rod L1 and the second connecting rod L2 are not equal.

[0069] Furthermore, there is a first included angle A between the first link L1 and the second link L2, and a second included angle B between the third link L3 and the fourth link L4, wherein the first included angle A is twice the second included angle B.

[0070] Furthermore, the line connecting the axis O0 of the first segment, the axis O0' of the second segment, the axis O1 of the first cross-groove segment, and the axis O1' of the second cross-groove segment is the connecting line O0 O0'O1 O1'. The first connecting rod L1 has a third included angle C with the connecting line O0 O0'O1 O1', and the corresponding third connecting rod L3 has a fourth included angle D with the connecting line O0 O0'O1 O1', wherein the third included angle C is twice the fourth included angle D; the second connecting rod L2 has a fifth included angle E with the connecting line O0 O0'O1 O1', and the corresponding fourth connecting rod L4 has a sixth included angle F with the connecting line O0 O0'O1 O1', wherein the fifth included 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, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

[0071] Furthermore, the operating method also includes the slider's rotational angular velocity being the same as its revolution angular velocity; and the revolution angular velocity of the first and second intersecting slot sections being the same as the slider's rotational angular velocity.

[0072] Furthermore, during the crankshaft rotation, the crankshaft rotates 2 revolutions, completing 4 intake and exhaust processes.

[0073] By applying the technical solution of this invention, the cross-groove structure is configured with two limiting channels, and two sliders are correspondingly provided. The two eccentric parts of the crankshaft extend into the two through holes of the two sliders. At the same time, the two sliders are slidably disposed in the two limiting channels to form a variable volume cavity. Since the first included angle A between the two eccentric parts is twice the second included angle B between the extension directions of the two limiting channels, when one of the two sliders is in a dead position, that is, the driving torque of the eccentric part corresponding to the slider in the dead position is 0, the slider in the dead position cannot continue to rotate. At this time, the driving torque of the other eccentric part driving the corresponding slider is at its maximum value, ensuring that the eccentric part with the maximum driving torque can normally drive the corresponding slider to rotate. Thus, the slider drives the cross-groove structure to rotate, and the cross-groove structure drives the slider in the dead position to continue to rotate. This achieves stable operation of the fluid machinery, avoids the dead position of the motion mechanism, and improves the motion reliability of the fluid machinery.

[0074] Furthermore, since the fluid machinery provided in this application can operate stably, that is, it ensures that the compressor has high energy efficiency and low noise, thereby ensuring the reliability of the heat exchange equipment. Attached Figure Description

[0075] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0076] Figure 1 A schematic diagram illustrating the operating principle of a compressor according to Embodiment 1 of the present invention is shown;

[0077] Figure 2 It shows Figure 1 A schematic diagram illustrating the operating principle of the compressor in the diagram;

[0078] Figure 3 A schematic diagram of the internal structure of a compressor according to an optional embodiment of the present invention is shown;

[0079] Figure 4 It shows Figure 3 A schematic diagram of the pump body assembly of the compressor in the image;

[0080] Figure 5 It shows Figure 4 An exploded view of the pump body components;

[0081] Figure 6 It shows Figure 5 A schematic diagram of the cross-groove structure and the slider in the exploded state;

[0082] Figure 7 It shows Figure 6 A schematic diagram of the first cross-groove segment of the cross-groove structure in the diagram;

[0083] Figure 8 It shows Figure 6 A schematic diagram of the second cross-groove segment of the cross-groove structure;

[0084] Figure 9 It shows Figure 6 A schematic diagram of the first sliding connector in the cross-groove structure;

[0085] Figure 10 It shows Figure 4 A structural diagram of the crankshaft, cross groove structure, and slider in the diagram;

[0086] Figure 11 It shows Figure 5 A schematic diagram of the crankshaft structure in the diagram;

[0087] Figure 12 It shows Figure 11 A cross-sectional view of the crankshaft in the diagram;

[0088] Figure 13 It shows Figure 5An exploded view of the upper flange, cylinder liner, and lower flange.

[0089] Figure 14 It shows Figure 5 A schematic diagram showing the eccentricity of the first and second sections of the crankshaft with respect to the cylinder liner.

[0090] Figure 15 It shows Figure 14 A cross-sectional structural diagram from the OO perspective;

[0091] Figure 16 It shows Figure 5 A schematic diagram of the structure of the first slider in the axial direction of its through hole;

[0092] Figure 17 It shows Figure 5 A schematic diagram of the structure of the second slider in the axial direction of its through hole;

[0093] Figure 18 It shows Figure 13 A structural schematic diagram of the cylinder liner from another perspective;

[0094] Figure 19 It shows Figure 18 A schematic diagram of the cross-sectional structure from the PP perspective;

[0095] Figure 20 It shows Figure 18 A first-view sectional structural diagram of the cylinder liner;

[0096] Figure 21 It shows Figure 18 A cross-sectional view of the cylinder liner from a second perspective;

[0097] Figure 22 It shows Figure 5 A schematic diagram of the exploded structure of the cylinder liner and exhaust cover;

[0098] Figure 23 It shows Figure 3 A schematic diagram of the compressor in the intake state.

[0099] Figure 24 It shows Figure 3 A schematic diagram of the compressor in the intake process.

[0100] Figure 25 It shows Figure 3 A schematic diagram of the compressor in the state at the end of the intake phase;

[0101] Figure 26 It shows Figure 3 A schematic diagram of the compressor's state when it is compressing gas;

[0102] Figure 27 It shows Figure 3 A schematic diagram of the compressor in the exhaust process.

[0103] Figure 28 It shows Figure 3 A schematic diagram of the compressor in the state at the end of exhaust;

[0104] Figure 29 A schematic diagram illustrating the operating principle of the compressor according to Embodiment 2 of the present invention is shown;

[0105] Figure 30 It shows Figure 29 A schematic diagram illustrating the operating principle of the compressor in the diagram;

[0106] Figure 31 A schematic diagram illustrating the operating principle of the compressor according to Embodiment 3 of the present invention is shown;

[0107] Figure 32 It shows Figure 31 A schematic diagram illustrating the operating principle of the compressor in the diagram;

[0108] Figure 33 A schematic diagram of the internal structure of a compressor according to an optional embodiment of the present invention is shown;

[0109] Figure 34 It shows Figure 33 A schematic diagram of the pump body assembly of the compressor in the image;

[0110] Figure 35 It shows Figure 34 An exploded view of the pump body components;

[0111] Figure 36 It shows Figure 35 A schematic diagram of the assembly structure of the crankshaft, cross groove structure, and slider;

[0112] Figure 37 It shows Figure 36 A cross-sectional view of the crankshaft, cross groove structure, and slider in the diagram;

[0113] Figure 38 It shows Figure 35 A partial structural diagram of the crankshaft in the diagram;

[0114] Figure 39 It shows Figure 38 A schematic diagram of the first section of the crankshaft in the image;

[0115] Figure 40 It shows Figure 39 A cross-sectional view of the crankshaft in the diagram;

[0116] Figure 41 It shows Figure 38 A schematic diagram of the second section of the crankshaft in the diagram;

[0117] Figure 42 It shows Figure 41 A cross-sectional view of the crankshaft in the diagram;

[0118] Figure 43 It shows Figure 5 An exploded view of the upper flange, cylinder liner, and lower flange.

[0119] Figure 44 It shows Figure 5 A schematic diagram showing the eccentricity of the first and second sections of the crankshaft with respect to the cylinder liner.

[0120] Figure 45 It shows Figure 14 A schematic diagram of the cross-sectional structure from the NN perspective;

[0121] Figure 46 A schematic diagram illustrating the operating principle of a compressor in the prior art is shown;

[0122] Figure 47 A schematic diagram illustrating the operating principle of the improved compressor in the prior art is shown.

[0123] Figure 48 It shows Figure 47 The diagram shows the mechanism of the compressor in operation, which illustrates the lever arm that drives the slider to rotate.

[0124] Figure 49 It shows Figure 47 The diagram shows the operating principle of the compressor mechanism. In this diagram, the center of the limiting groove structure and the center of the eccentric part coincide.

[0125] The above figures include the following reference numerals:

[0126] 10. Crankshaft; 11. Eccentric part; 12. Shaft body part; 121. First section; 1211. First protruding structure; 122. Second section; 1221. Second protruding structure; 13. Sliding connector; 131. Limiting groove;

[0127] 20. Cylinder liner; 21. Compression intake port; 22. Compression exhaust port; 23. Intake chamber; 24. Intake connecting chamber; 25. Exhaust chamber; 26. Connecting hole;

[0128] 30. Cross-groove structure; 31. Limiting channel; 311. Variable volume cavity; 32. Center hole; 33. First cross-groove section; 331. Third protrusion structure; 34. Second cross-groove section; 341. Fourth protrusion structure; 35. First sliding connector; 351. First limiting groove;

[0129] 40. Slider; 41. Through hole; 42. Extrusion surface;

[0130] 50. Flange; 51. Venting channel; 52. Upper flange; 53. Lower flange;

[0131] 60. Exhaust valve assembly; 61. Exhaust valve plate; 62. Valve plate baffle;

[0132] 70. Exhaust cover;

[0133] 80. Dispenser assembly; 81. Housing assembly; 82. Motor assembly; 83. Pump body assembly; 84. Top cover assembly; 85. Bottom cover assembly;

[0134] 90. Fasteners. Detailed Implementation

[0135] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0136] In existing technologies, such as Figure 46 As shown, a compressor operating mechanism principle is proposed based on the cross slider mechanism. Specifically, point O1 is used as the cylinder center, point O2 as the drive shaft center, and point O3 as the slider center. The cylinder and drive shaft are eccentrically set, and the slider center O3 moves in a circle with a diameter of O1O2.

[0137] In the above operating mechanism principle, the cylinder center O1 and the drive shaft center O2 serve as the two rotation centers of the motion mechanism. At the same time, the midpoint O0 of the line segment O1O2 serves as the virtual center of the slider center O3, so that while the slider reciprocates relative to the cylinder, it also reciprocates relative to the drive shaft.

[0138] Because the midpoint O0 of line segment O1O2 is a virtual center, a balancing system cannot be set up, leading to a deterioration of the compressor's high-frequency vibration characteristics. Based on the above operating mechanism principle, as follows... Figure 47As shown, a motion mechanism with O0 as the center of the drive shaft is proposed. That is, the cylinder center O1 and the drive shaft center O0 are the two rotation centers of the motion mechanism. The drive shaft has an eccentric part, and the slider is coaxially arranged with the eccentric part. The assembly eccentricity of the drive shaft and the cylinder is equal to the eccentricity of the eccentric part, so that the slider center O3 moves in a circle with the drive shaft center O0 as the center and O1O0 as the radius.

[0139] A corresponding operating mechanism is proposed, including a cylinder, a limiting groove structure, a slider, and a drive shaft. The limiting groove structure is rotatably mounted inside the cylinder, and the cylinder and the limiting groove structure are coaxially arranged, that is, the center O1 of the cylinder is also the center of the limiting groove structure. The slider reciprocates relative to the limiting groove structure. The slider is coaxially assembled with the eccentric part of the drive shaft. The slider performs circumferential motion around the shaft body of the drive shaft. Specifically, the motion process is as follows: the drive shaft rotates, causing the slider to revolve around the center of the shaft body of the drive shaft. At the same time, the slider rotates relative to the eccentric part. The slider reciprocates within the limiting groove of the limiting groove structure and pushes the limiting groove structure to rotate.

[0140] However, as Figure 48 As shown, the length of the lever arm L that drives the slider to rotate is L = 2e × cosθ × cosθ, where e is the eccentricity of the eccentric part and θ is the angle between the line connecting O1O0 and the sliding direction of the slider in the limiting groove.

[0141] like Figure 49 As shown, when the cylinder center O1 (i.e., the center of the limiting groove structure) coincides with the center of the eccentric part, the resultant force of the driving force of the drive shaft passes through the center of the limiting groove structure. That is, the torque applied to the limiting groove structure is zero, the limiting groove structure cannot rotate, and the motion mechanism is at a dead point position and cannot drive the slider to rotate.

[0142] Based on this, this application proposes a novel cross-slot structure with two limiting channels and a double slider mechanism, and constructs a novel compressor based on this principle. This compressor has the characteristics of high energy efficiency and low noise. The following uses the compressor as an example to specifically introduce the compressor based on the cross-slot structure with two limiting channels and the double slider.

[0143] To address the issues of low energy efficiency and high noise levels in existing compressors, this invention provides a fluid machine, a heat exchange device, and a method for operating the fluid machine. The heat exchange device includes the fluid machine described below, and the fluid machine is operated using the method described below.

[0144] The fluid machinery of this invention includes a crankshaft 10, a cylinder liner 20, a cross-groove structure 30, and a slider 40. The crankshaft 10 has two eccentric portions 11 along its axial direction, with a phase difference of a first included angle A between the two eccentric portions 11. The crankshaft 10 and the cylinder liner 20 are eccentrically positioned with a fixed eccentric distance. The cross-groove structure 30 is rotatably disposed within the cylinder liner 20. The cross-groove structure 30 includes a first cross-groove segment 33 and a second cross-groove segment 34 connected along its axial direction. The first cross-groove segment 33 and the second cross-groove segment 34 are coaxially arranged and movably connected. Both the first cross-groove segment 33 and the second cross-groove segment 34 have limiting channels 31, which are sequentially arranged along the axial direction of the crankshaft 10. The extension direction of the positioning channel 31 is perpendicular to the axial direction of the crankshaft 10, and there is a phase difference of a second included angle B between the extension directions of the two positioning channels 31, wherein the first included angle A is twice the second included angle B; the slider 40 has a through hole 41, and there are two sliders 40. The two eccentric parts 11 extend into the two through holes 41 of the two sliders 40 respectively. The two sliders 40 are slidably disposed in the two positioning 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 positioning channel 31 while interacting with the cross groove structure 30, so that the cross groove structure 30 and the slider 40 rotate in the cylinder liner 20.

[0145] By configuring the cross-groove structure 30 into a structure with two limiting channels 31 and correspondingly arranging two sliders 40, the two eccentric portions 11 of the crankshaft extend into the two through holes 41 of the two sliders 40. Simultaneously, the two sliders 40 are slidably disposed within the two limiting channels 31, forming a variable volume cavity 311. Since the first included angle A between the two eccentric portions 11 is twice the second included angle B between the extending directions of the two limiting channels 31, when one of the two sliders 40 is at a dead position, i.e., the driving torque of the eccentric portion 11 corresponding to the slider 40 at the dead position... When the value is 0, the slider 40 at the dead point position cannot continue to rotate. At this time, the driving torque of the other eccentric part 11 driving the corresponding slider 40 is at its maximum value, ensuring that the eccentric part 11 with the maximum driving torque can normally drive the corresponding slider 40 to rotate. This slider 40 drives the cross groove structure 30 to rotate, and then the cross groove structure 30 drives the slider 40 at the dead point position to continue to rotate. This achieves stable operation of the fluid machinery, avoids the dead point position of the motion mechanism, improves the motion reliability of the fluid machinery, and thus ensures the working reliability of the heat exchange equipment.

[0146] Furthermore, since the fluid machinery provided in this application can operate stably, that is, it ensures that the compressor has high energy efficiency and low noise, thereby ensuring the reliability of the heat exchange equipment.

[0147] It should be noted that in this application, neither the first included angle A nor the second included angle B is zero.

[0148] Example 1

[0149] like Figure 1 and Figure 2 As shown, when the aforementioned fluid machinery is running, the crankshaft 10 rotates around its axis O0; the first cross-groove section 33 revolves around the axis O0 of the crankshaft 10, with the axis O0 of the crankshaft 10 eccentrically positioned with a fixed eccentricity to the axis O1 of the first cross-groove section 33; the second cross-groove section 34 revolves around the axis O0 of the crankshaft 10, with the axis O0 of the crankshaft 10 eccentrically positioned with a fixed eccentricity to the axis O1' of the second cross-groove section 34; the first slider 40 moves in a circular motion with the axis O0 of the crankshaft 10 as its center, and the distance between the center O3 of the first slider 40 and the axis O0 of the crankshaft 10 is equal to the eccentricity of the first eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the distance between the axis O0 of the crankshaft 10 and the axis O1 of the first cross-groove section 33. The crankshaft 10 rotates to drive the first slider 40 to make a circular motion, and the first slider 40 interacts with the first cross groove section 33 and slides back and forth in the limiting channel 31 of the first cross groove section 33; the second slider 40 makes a circular motion with the axis O0 of the crankshaft 10 as the center, and the distance between the center O4 of the second slider 40 and the axis O0 of the crankshaft 10 is equal to the eccentricity of the second eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentric distance between the axis O0 of the crankshaft 10 and the axis O1' of the second cross groove section 34. The crankshaft 10 rotates to drive the second slider 40 to make a circular motion, and the second slider 40 interacts with the second cross groove section 34 and slides back and forth in the limiting channel 31 of the second cross groove section 34.

[0150] The fluid machinery operating under the first operating method described above constitutes a cross-slider mechanism. This operating method adopts the principle of the cross-slider mechanism, wherein the two eccentric parts 11 of the crankshaft 10 serve as the first connecting rod L1 and the second connecting rod L2, respectively; the limiting channel 31 of the first cross groove section 33 serves as the third connecting rod L3; and the limiting channel 31 of the second cross groove section 34 serves as the fourth connecting rod L4. The lengths of the first connecting rod L1 and the second connecting rod L2 are not equal.

[0151] like Figure 1 As shown, there is a first included angle A between the first link L1 and the second link L2, and a second included angle B between the third link L3 and the fourth link L4, wherein the first included angle A is twice the second included angle B.

[0152] like Figure 2As shown, the line connecting the crankshaft 10's axis O0, the first cross groove section 33's axis O1, and the second cross groove section 34's axis O1' is line O0O1O1'. The first connecting rod L1 has a third included angle C with line O0O1O1', and the corresponding third connecting rod L3 has a fourth included angle D with line O0O1O1', where the third included angle C is twice the fourth included angle D. The second connecting rod L2 has a fifth included angle E with line O0O1O1', and the corresponding fourth connecting rod L4 has a sixth included angle F with line O0O1O1', where the fifth included 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, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

[0153] Furthermore, the operating method also includes the fact that the rotational angular velocity of the slider 40 is the same as the revolution angular velocity of the slider 40; and the revolution angular velocity of the first cross groove segment 33 and the second cross groove segment 34 is the same as the rotational angular velocity of the slider 40.

[0154] Specifically, the axis O0 of the crankshaft 10 corresponds to the rotation center of the first connecting rod L1 and the second connecting rod L2, the axis O1 of the first cross groove section 33 corresponds to the rotation center of the third connecting rod L3, and the axis O1' of the second cross groove section 34 corresponds to the rotation center of the fourth connecting rod L4. The two eccentric parts 11 of the crankshaft 10 serve as the first connecting rod L1 and the second connecting rod L2, respectively, and the two limiting channels 31 of the cross groove structure 30 serve as the third connecting rod L3 and the fourth connecting rod L4, respectively. The lengths of the first connecting rod L1 and the second connecting rod L2 are equal. Thus, while the crankshaft 10 rotates, the eccentric parts 11 on the crankshaft 10 drive the corresponding slider 40 to revolve around the axis O0 of the crankshaft 10. At the same time, the slider 40 can rotate relative to the eccentric parts 11, and the relative rotation speeds of the two are the same. Since the first slider 40 and the second slider... The two sliders 40 reciprocate within their respective limiting channels 31, causing the cross-groove structure 30 to rotate. Limited by the two limiting channels 31 of the cross-groove structure 30, the movement directions of the two sliders 40 always have a phase difference of the second included angle B. When one of the two sliders 40 is at a dead position, the eccentric part 11 used to drive the other slider 40 has the maximum driving torque. The eccentric part 11 with the maximum driving torque can normally drive the corresponding slider 40 to rotate, thereby driving the cross-groove structure 30 to rotate. This, in turn, drives the slider 40 at the dead position to continue rotating, achieving stable operation of the fluid machinery, avoiding the dead position of the motion mechanism, improving the motion reliability of the fluid machinery, and thus ensuring the working reliability of the heat exchange equipment.

[0155] It should be noted that in this application, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 revolutions, completing 4 intake and exhaust processes.

[0156] Under this motion method, the running trajectory of each slider 40 is a circle. One circle has the axis O0 of the crankshaft 10 as its center and the line O0 O1 as its radius, and the other circle has the axis O0 of the crankshaft 10 as its center and the line O0 O1' as its radius.

[0157] It should be noted that in this application, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 revolutions, completing 4 intake and exhaust processes.

[0158] An optional implementation will be given below to provide a detailed description of the structure of the fluid machinery, so as to better illustrate the operation method of the fluid machinery through its structural features.

[0159] It should be noted that, in this application, the distance between the inner ring axis of the cylinder liner 20 located at the first cross groove section 33 and the inner ring axis of the cylinder liner 20 located at the second cross groove section 34 is equal to the eccentric distance between the first cross groove section 33 and the second cross groove section 34. This ensures that... Figure 1 The normal operation of the constructed motion mechanism.

[0160] like Figures 4 to 10 As shown, the cross-slot structure 30 also includes a first sliding connector 35. The first cross-slot segment 33 is movably connected to the second cross-slot segment 34 via the first sliding connector 35. When the first cross-slot segment 33 rotates, the first sliding connector 35 slides relative to the first cross-slot segment 33. When the second cross-slot segment 34 rotates, the first sliding connector 35 slides relative to the second cross-slot segment 34. In this way, the connection reliability of the first cross-slot segment 33 and the second cross-slot segment 34 are ensured, as well as the rotational reliability between them.

[0161] like Figures 7 to 9As shown, the first sliding connector 35 has two first limiting grooves 351, the extension directions of which are both perpendicular to the axial direction of the crankshaft 10, and the extension directions of the two first limiting grooves 351 are perpendicular to each other; the end of the first cross groove section 33 facing the first sliding connector 35 has a third protrusion structure 331, and the end of the second cross groove section 34 facing the first sliding connector 35 has a fourth protrusion structure 341, the third protrusion structure 331 and the fourth protrusion structure 341 are slidably disposed in the two first limiting grooves 351 respectively; the first cross groove section 33 rotates to make the third protrusion structure 331... While reciprocating within the corresponding first limiting groove 351, the fourth protruding structure 341 interacts with the first sliding connector 35. The first sliding connector 35 rotates, causing the fourth protruding structure 341 to reciprocate within the corresponding first limiting groove 351, simultaneously driving the second cross groove segment 34 to rotate. Alternatively, the second cross groove segment 34 rotates so that the fourth protruding structure 341 reciprocates within the corresponding first limiting groove 351 while interacting with the first sliding connector 35. The first sliding connector 35 rotates, causing the third protruding structure 331 to reciprocate within the corresponding first limiting groove 351, simultaneously driving the first cross groove segment 33 to rotate. This ensures both the reliable connection between the first cross groove segment 33 and the second cross groove segment 34, and guarantees the reliable rotation between them.

[0162] It should be noted that, in an embodiment not shown in this application, the first sliding connector 35 has two first limiting protrusions extending toward the first cross groove segment 33 and the second cross groove segment 34, respectively; the end of the first cross groove segment 33 facing the first sliding connector 35 has a third sliding groove structure, and the end of the second cross groove segment 34 facing the first sliding connector 35 has a fourth sliding groove structure. The two first limiting protrusions are slidably disposed within the third and fourth sliding groove structures, respectively, and the extending direction of the third sliding groove structure is perpendicular to the extending direction of the fourth sliding groove structure; the first cross groove segment 33 rotates to... While the corresponding first limiting protrusion reciprocates within the third sliding groove structure, the third sliding groove structure interacts with the first sliding connector 35. The first sliding connector 35 rotates, causing the first limiting protrusion to reciprocate within the fourth sliding groove structure, simultaneously driving the second intersecting groove segment 34 to rotate. Alternatively, the second intersecting groove segment 34 rotates, causing the corresponding first limiting protrusion to reciprocate within the fourth sliding groove structure. Simultaneously, the fourth sliding groove structure interacts with the first sliding connector 35, causing the first sliding connector 35 to rotate, causing the first limiting protrusion to reciprocate within the third sliding groove structure, simultaneously driving the first intersecting groove segment 33 to rotate. This ensures both the reliable connection between the first intersecting groove segment 33 and the second intersecting groove segment 34 and the reliable rotation between them.

[0163] like Figures 10 to 12As shown, the crankshaft 10 has a single integral shaft body 12, and the shaft body 12 has only one shaft center. This facilitates the one-time molding of the shaft body 12, thereby reducing the difficulty of machining and manufacturing the shaft body 12.

[0164] It should be noted that, in an embodiment of this application not shown, 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 two eccentric portions 11 are respectively arranged on the first section and the second section.

[0165] Optionally, the first and second sections can be detachably connected. This ensures ease of assembly and disassembly of the crankshaft 10.

[0166] like Figure 12 and Figure 14 As shown, the eccentricities of the two eccentric portions 11 are not equal. The eccentricity of the first eccentric portion 11 is equal to the assembly eccentricity of the crankshaft 10 with the corresponding first cross groove segment 33; the eccentricity of the second eccentric portion 11 is equal to the assembly eccentricity of the crankshaft 10 with the corresponding second cross groove segment 34. This ensures the construction... Figure 1 The motion mechanism within is functioning normally.

[0167] like Figures 10 to 12 As shown, the shaft body portion 12 and the eccentric portion 11 of the crankshaft 10 are integrally formed. This facilitates the one-time forming of the crankshaft 10, thereby reducing the difficulty of machining and manufacturing the crankshaft 10.

[0168] It should be noted that, in an embodiment not shown in this application, the shaft portion 12 of the crankshaft 10 is detachably connected to the eccentric portion 11. This facilitates the installation and removal of the eccentric portion 11.

[0169] like Figures 5 to 8 As shown, one of the two limiting channels 31 extends to the outer periphery of the first cross groove section 33 at both ends, and the other of the two limiting channels 31 extends to the outer periphery of the second cross groove section 34 at both ends. This helps to reduce the processing and manufacturing difficulty of the cross groove structure 30.

[0170] Optionally, the two sliders 40 are respectively concentrically arranged with the two eccentric parts 11. The sliders 40 move in a circular motion around the axis of the crankshaft 10 of the eccentric part 11. There is a first rotational gap between the hole wall of the through hole 41 and the eccentric part 11. The range of the first rotational gap is 0.005mm to 0.05mm.

[0171] Optionally, a second rotational clearance exists between the outer peripheral surface of the first cross groove section 33 and the inner wall surface of one axial end of the cylinder liner 20, the second rotational clearance being in the range of 0.01mm to 0.08mm; and a third rotational clearance exists between the outer peripheral surface of the second cross groove section 34 and the inner wall surface of the other axial end of the cylinder liner 20, the third rotational clearance being in the range of 0.01mm to 0.08mm.

[0172] It should be noted that in this application, the first included angle A is 160 degrees to 200 degrees; the second included angle B is 80 degrees to 100 degrees. Thus, it is sufficient to satisfy the relationship that the first included angle A is twice the second included angle B.

[0173] Preferably, the first included angle A is 160 degrees and the second included angle B is 80 degrees.

[0174] Preferably, the first included angle A is 165 degrees and the second included angle B is 82.5 degrees.

[0175] Preferably, the first included angle A is 170 degrees and the second included angle B is 85 degrees.

[0176] Preferably, the first included angle A is 175 degrees and the second included angle B is 87.5 degrees.

[0177] Preferably, the first included angle A is 180 degrees and the second included angle B is 90 degrees.

[0178] Preferably, the first included angle A is 185 degrees and the second included angle B is 92.5 degrees.

[0179] Preferably, the first included angle A is 190 degrees and the second included angle B is 95 degrees.

[0180] Preferably, the first included angle A is 195 degrees and the second included angle B is 97.5 degrees.

[0181] like Figures 3 to 28 As shown, the fluid machinery also includes a flange 50, which is located at the axial end of the cylinder liner 20. The crankshaft 10 is concentrically arranged with the flange 50, and the cross groove structure 30 is coaxially arranged with the cylinder liner 20. 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 to the cylinder liner 20 by fasteners 90. The relative position of the axis of the flange 50 and the axis of the inner ring of the cylinder liner 20 is controlled by the flange 50 self-aligning. The relative position of the axis of the flange 50 and the axis of the inner ring of the cylinder liner 20 determines the relative position of the axis of the crankshaft 10 and the axis of the cross groove structure 30. The essence of self-aligning the flange 50 is to make the eccentricity of the eccentric part 11 equal to the assembly eccentricity of the crankshaft 10 and the cylinder liner 20.

[0182] Specifically, such as Figure 12As shown, the eccentricity of the first eccentric part 11 is equal to e1, and the eccentricity of the second eccentric part 11 is equal to e2, as... Figure 14 and Figure 15 As shown, the assembly eccentricity between the first section of crankshaft 10 and cylinder liner 20 is e1, and the assembly eccentricity between the second section of crankshaft 10 and cylinder liner 20 is e2 (since the cross-groove structure 30 is coaxially arranged with cylinder liner 20, the assembly eccentricity between crankshaft 10 and cross-groove structure 30 is the same as the assembly eccentricity between crankshaft 10 and cylinder liner 20). Figure 15 In the diagram, H indicates the axis of the crankshaft 10's shaft body 12, I indicates the axis of the upper half of the cylinder liner 20's inner ring, and J indicates the axis of the lower half of the cylinder liner 20's inner ring. Flange 50 includes an upper flange 52 and a lower flange 53, as shown below. Figure 11 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, which is equal to the eccentricity of the eccentric part 11.

[0183] Optionally, a first assembly gap is provided between the crankshaft 10 and the flange 50, the first assembly gap being in the range of 0.005mm to 0.05mm.

[0184] Preferably, the range of the first assembly gap is 0.01 to 0.03 mm.

[0185] It should be noted that in this application, the eccentric portion 11 has an arc surface, and the central angle of the arc surface is greater than or equal to 180 degrees. This ensures that the arc surface of the eccentric portion 11 can apply an effective driving force to the slider 40, thereby ensuring the reliability of the slider 40's movement.

[0186] like Figures 10 to 12 As shown, the eccentric part 11 is cylindrical.

[0187] Optionally, the proximal end of the eccentric portion 11 is flush with the outer circle of the shaft portion 12 of the crankshaft 10.

[0188] Optionally, the proximal end of the eccentric portion 11 protrudes beyond the outer circle of the shaft portion 12 of the crankshaft 10.

[0189] Optionally, the proximal end of the eccentric portion 11 is located inside the outer circle of the shaft portion 12 of the crankshaft 10.

[0190] It should be noted that, in one embodiment of this application (not shown), the slider 40 includes multiple substructures, which are spliced ​​together to form a through hole 41.

[0191] like Figures 10 to 12 As shown, the two eccentric portions 11 are spaced apart axially on the crankshaft 10. This ensures that during the assembly of the crankshaft 10, cylinder liner 20, and two sliders 40, the spacing between the two eccentric portions 11 provides sufficient assembly space for the cylinder liner 20, thus ensuring ease of assembly.

[0192] like Figure 7 and Figure 8 As shown, both the first cross groove section 33 and the second cross groove section 34 have a center hole 32. The two center holes 32 are not concentrically arranged, and the two limiting channels 31 are connected through the two center holes 32. The diameter of each center hole 32 is larger than the diameter of the shaft portion 12 of the crankshaft 10. This ensures that the crankshaft 10 can pass smoothly through the center hole 32.

[0193] Optionally, the diameter of the central hole 32 is larger than the diameter of the eccentric portion 11. This ensures that the eccentric portion 11 of the crankshaft 10 can pass smoothly through the central hole 32.

[0194] like Figure 16 and Figure 17 As shown, the projection of slider 40 in the axial direction of 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 opposing first sliding surfaces that slide in contact with slider 40. Slider 40 has a second sliding surface that mates with the first sliding surface. Slider 40 has a pressing surface 42 facing the end of limiting channel 31, which serves as the head of slider 40. The two second sliding surfaces are connected by the pressing surface 42, which faces the variable volume cavity 311. Thus, the projection of the second sliding surface of slider 40 in the axial direction of its through hole 41 is a straight line segment, while the projection of the pressing surface 42 of slider 40 in the axial direction of its through hole 41 is an arc segment.

[0195] Specifically, the extrusion surface 42 is an arc surface, and the distance between the center of the arc surface and the center of the through hole 41 is equal to the eccentricity of the eccentric part 11. For example... Figure 16 and Figure 17 As shown, the center of the through hole 41 of the slider 40 is O. 滑块 The distances between the center of the two arc surfaces and the center of the corresponding through holes 41 are e1 and e2, respectively. That is, the eccentricity e1 of the eccentric part 11 on the first section 121 of the corresponding crankshaft 10 and the eccentricity e2 of the eccentric part 11 on the second section 122 are respectively. Figure 16 The dashed X-line in the diagram represents the circle containing the center of the two arc surfaces.

[0196] Optionally, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20.

[0197] Optionally, the radius of curvature of the arc surface has a difference from the radius of the inner circle of the cylinder liner 20, and the difference ranges from -0.05mm to 0.025mm.

[0198] Preferably, the difference ranges from -0.02 to 0.02 mm.

[0199] Optionally, the projected area S of the extrusion surface 42 in the sliding direction of the slider 40 is...滑块 The area of ​​the compression exhaust port of cylinder liner 20 is S 排 The following conditions must be met between them: S 滑块 / S 排 The value is 8 to 25.

[0200] Preferably, S 滑块 / S 排 The value is 12 to 18.

[0201] It should be noted that the fluid machinery shown in this embodiment is a compressor, such as... Figure 3 As shown, the compressor includes a distributor component 80, a housing assembly 81, a motor assembly 82, a pump body assembly 83, an upper cover assembly 84, and a lower cover assembly 85. The distributor component 80 is located outside the housing assembly 81. The upper cover assembly 84 is mounted on the upper end of the housing assembly 81, and the lower cover assembly 85 is mounted on the lower end of the housing assembly 81. The motor assembly 82 and the pump body assembly 83 are both located inside the housing assembly 81, with the motor assembly 82 located either above or below the pump body assembly 83. The pump body assembly 83 of the compressor includes the aforementioned crankshaft 10, cylinder liner 20, cross-groove structure 30, slider 40, upper flange 52, and lower flange 53.

[0202] Alternatively, the above-mentioned components can be connected by welding, heat fitting, or cold pressing.

[0203] The assembly process of the entire pump body assembly 83 is as follows: The lower flange 53 is fixed on the cylinder liner 20. One slider 40 is placed in the limiting channel 31 of the second cross groove section 34, and then both are placed into the cylinder liner 20. The first sliding connector 35 is placed into the cylinder liner 20 and assembled with the second cross groove section 34. Then, another slider 40 is placed in the limiting channel 31 of the first cross groove section 33, and then both are placed into the cylinder liner 20 and assembled with the first sliding connector 35. The two eccentric parts 11 of the crankshaft 10 extend into the two through holes 41 of the corresponding two sliders 40. Then, the assembled crankshaft 10, cross groove structure 30 and two sliders 40 are placed into the cylinder liner 20. One end of the crankshaft 10 is mounted on the lower flange 53, and the other end of the crankshaft 10 passes through the upper flange 52. For details, please refer to [link to documentation]. Figure 4 and Figure 5 .

[0204] It should be noted that in this embodiment, the enclosed space formed 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 4 variable volume chambers 311. During the rotation of the crankshaft 10, the crankshaft 10 rotates 2 times, and a single variable volume chamber 311 completes 1 intake and exhaust process. For the compressor, the crankshaft 10 rotates 2 times, and a total of 4 intake and exhaust processes are completed.

[0205] like Figures 23 to 28 As shown, during the reciprocating motion of the slider 40 within the limiting channel 31, it simultaneously rotates relative to the cylinder liner 20. Figures 23 to 25 During the clockwise rotation of slider 40 from 0 degrees to 180 degrees, the variable volume cavity 311 increases in size. As the variable volume cavity 311 increases, it connects with the intake cavity 23 of cylinder liner 20. When slider 40 rotates to 180 degrees, the volume of the variable volume cavity 311 reaches its maximum value, at which point it disengages from the intake cavity 23, thus completing the intake operation. Figures 26 to 28 During the process of slider 40 continuing to rotate clockwise from 180 degrees to 360 degrees, the variable volume chamber 311 decreases, and slider 40 compresses the gas in the variable volume chamber 311. When slider 40 rotates to the point where the variable volume chamber 311 is connected to the compression exhaust port 22, and when the gas in the variable volume chamber 311 reaches the exhaust pressure, the exhaust valve plate 61 of the exhaust valve assembly 60 opens, and the exhaust operation begins until the compression is completed and the next cycle begins. The valve plate baffle 62 of the exhaust valve assembly 60 acts as a shield for the exhaust valve plate 61, preventing the valve plate baffle 62 from deforming too much.

[0206] like Figures 23 to 28 As shown, the point marked M is used as the reference point for the relative motion between slider 40 and crankshaft 10. Figure 24 This represents the process of slider 40 rotating clockwise from 0 degrees to 180 degrees. The angle of rotation of slider 40 is θ1, and the corresponding angle of rotation of crankshaft 10 is 2θ1. Figure 26 The diagram shows the process of slider 40 continuing to rotate clockwise from 180 degrees to 360 degrees. The rotation angle of slider 40 is 180° + θ2, and the corresponding rotation angle of crankshaft 10 is 360° + 2θ2. Figure 27 The diagram shows the process of slider 40 continuing to rotate clockwise from 180 degrees to 360 degrees, and the variable volume cavity 311 is connected to the compression exhaust port 22. The angle of rotation of slider 40 is 180°+θ3, and the corresponding angle of rotation of crankshaft 10 is 360°+2θ3. That is, when slider 40 rotates 1 revolution, the corresponding crankshaft 10 rotates 2 revolutions, where θ1 < θ2 < θ3.

[0207] Specifically, such as Figure 13 , Figures 18 to 26 As shown, the cylinder liner 20 has a compression intake port 21 and a compression exhaust port 22. When any slider 40 is in the intake position, the compression intake port 21 is connected to the corresponding variable volume chamber 311; when any slider 40 is in the exhaust position, the corresponding variable volume chamber 311 is connected to the compression exhaust port 22.

[0208] like Figure 13 , Figures 18 to 26As shown, the inner wall of the cylinder liner 20 has an intake chamber 23, which is connected to the compression inlet 21. This ensures that the intake chamber 23 can store a large amount of gas, so that the variable volume chamber 311 can be fully saturated with gas, thereby enabling the compressor to draw in sufficient gas. When the intake is insufficient, the stored gas can be supplied to the variable volume chamber 311 in a timely manner to ensure the compression efficiency of the compressor.

[0209] Optionally, the intake chamber 23 is a cavity formed by radially hollowing out the inner wall surface of the cylinder liner 20. There can be one intake chamber 23 or two chambers, one above the other.

[0210] Specifically, the intake chamber 23 extends circumferentially around the inner wall of the cylinder liner 20 by a first predetermined distance to form an arc-shaped intake chamber 23. This ensures that the volume of the intake chamber 23 is large enough to store a large amount of gas.

[0211] like Figure 13 , Figures 20 to 22 As shown, there are two intake chambers 23, which are spaced apart along the axial direction of the cylinder liner 20. The cylinder liner 20 also has an intake connecting chamber 24, and both intake chambers 23 are connected to the intake connecting chamber 24. The compression inlet 21 is connected to the intake chambers 23 through the intake connecting chamber 24. This increases the volume of the intake chambers 23, thereby reducing intake pressure pulsation.

[0212] like Figure 18 and Figure 21 As shown, the intake communication cavity 24 extends a second predetermined distance along the axial direction of the cylinder liner 20, and at least one end of the intake communication cavity 24 penetrates the axial end face of the cylinder liner 20. This facilitates the opening of the intake communication cavity 24 from the end face of the cylinder liner 20, ensuring the ease of machining the intake communication cavity 24.

[0213] like Figure 13 , Figures 20 to 22 As shown, an exhaust chamber 25 is formed on the outer wall of the cylinder liner 20, and a compression exhaust port 22 is connected to the exhaust chamber 25 from the inner wall of the cylinder liner 20. The fluid machinery also includes an exhaust valve assembly, which is disposed in the exhaust chamber 25 and corresponding to the compression 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, makes the components more rationally arranged, and improves the space utilization of the cylinder liner 20.

[0214] like Figure 19 and Figure 21 As shown, there are two compression exhaust ports 22, which are spaced apart along the axial direction of the cylinder liner 20. There are two sets of exhaust valve assemblies, each corresponding to one of the two compression exhaust ports 22. In this way, since each of the two compression exhaust ports 22 is equipped with a separate set of exhaust valve assemblies, a large amount of gas leakage in the variable volume chamber 311 is effectively avoided, thus ensuring the compression efficiency of the variable volume chamber 311.

[0215] The exhaust valve assembly is connected to the cylinder liner 20 via fastener 90. The exhaust valve assembly includes an exhaust valve plate and a valve plate baffle. The exhaust valve plate is disposed within the exhaust chamber 25 and blocks the corresponding compressed exhaust port 22. The valve plate baffle overlaps and is disposed on the exhaust valve plate. In this way, the valve plate baffle effectively prevents the exhaust valve plate from over-opening, thereby ensuring the exhaust performance of the cylinder liner 20.

[0216] Optionally, fastener 90 is a screw.

[0217] like Figure 13 and Figure 22 As shown, a connecting hole 26 is also provided on the axial end face of the cylinder liner 20, which communicates with the exhaust chamber 25. The fluid machinery also includes a flange 50, on which an exhaust passage 51 is provided, and the connecting hole 26 communicates with the exhaust passage 51. This ensures the reliability of the exhaust of the cylinder liner 20.

[0218] like Figure 13 and Figure 22 As shown, the exhaust chamber 25 extends to the outer wall of the cylinder liner 20. The fluid machinery also includes an exhaust cover plate 70, which is connected to the cylinder liner 20 and seals the exhaust chamber 25. In this way, the exhaust cover plate 70 serves to separate the variable volume chamber 311 from the external space of the pump body assembly 83.

[0219] It should be noted that in this application, when the variable volume chamber 311 is connected to the compression exhaust port 22, when the pressure of the variable volume chamber 311 reaches the exhaust pressure, the exhaust valve plate opens, the compressed gas enters the exhaust chamber 25 through the compression exhaust port 22, passes through the connecting hole 26 on the cylinder liner 20, and is discharged through the exhaust passage 51 and enters the external space of the pump body assembly 83 (i.e., the compressor cavity), thereby completing the exhaust process.

[0220] Optionally, the exhaust cover 70 is secured to the cylinder liner 20 by fasteners 90.

[0221] Optionally, fastener 90 is a screw.

[0222] Optionally, the outer contour of the exhaust cover 70 is adapted to the outer contour of the exhaust chamber 25.

[0223] The following is a detailed introduction to the operation of the compressor:

[0224] like Figure 3As shown, the motor assembly 82 drives the crankshaft 10 to rotate. The two eccentric parts 11 of the crankshaft 10 drive the corresponding two sliders 40 to move. While the sliders 40 revolve around the axis of the crankshaft 10, the sliders 40 rotate relative to the eccentric parts 11. The sliders 40 reciprocate along the limiting channel 31 and drive the cross groove structure 30 to rotate inside the cylinder liner 20. The sliders 40 revolve along the limiting channel 31 while revolving, thus forming the cross slider mechanism motion mode.

[0225] Other applications: By switching the positions of the intake and exhaust ports, this compressor can be used as an expander. That is, the compressor's exhaust port is used as the expander's intake port, high-pressure gas is introduced, and other driving mechanisms rotate. After expansion, the gas is discharged through the compressor's intake port (expander's exhaust port).

[0226] When the fluid machinery is an expander, the cylinder liner 20 has an expansion exhaust port and an expansion intake port. When any slider 40 is in the intake position, the expansion exhaust port is connected to the corresponding variable volume chamber 311; when any slider 40 is in the exhaust position, the corresponding variable volume chamber 311 is connected to the expansion intake port.

[0227] Optionally, the inner wall surface of the cylinder liner 20 has an expansion exhaust chamber 25, which is connected to the expansion exhaust port.

[0228] Furthermore, the expansion exhaust chamber extends circumferentially around the inner wall of the cylinder liner 20 by a first predetermined distance to form an arc-shaped expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion intake port is located, and the extension direction of the expansion exhaust chamber is in the same direction as the rotation direction of the cross groove structure 30.

[0229] Furthermore, there are two expansion exhaust chambers, which are spaced apart along the axial direction of the cylinder liner 20. The cylinder liner 20 also has an expansion exhaust communication chamber, and both expansion exhaust chambers are connected to the expansion exhaust communication chamber. The expansion exhaust port is connected to the expansion exhaust chamber through the expansion exhaust communication chamber.

[0230] Furthermore, the expansion exhaust communication cavity extends a second predetermined distance along the axial direction of the cylinder liner 20, and at least one end of the expansion exhaust communication cavity penetrates the axial end face of the cylinder liner 20.

[0231] Example 2

[0232] like Figure 29 and Figure 30As shown, when the aforementioned fluid machinery is running, the first segment 121 of the crankshaft 10 rotates around its axis O0, and the second segment 122 of the crankshaft 10 rotates around its axis O0', wherein O0 and O0' do not coincide; the axis O0 of the first segment 121 is eccentrically positioned with a fixed eccentricity to the axis O1 of the first cross-groove segment 33, and the axis O0' of the second segment 122 is eccentrically positioned with a fixed eccentricity to the axis O1' of the second cross-groove segment 34; the first slider 40 moves in a circular motion with the axis O0 of the first segment 121 as its center, and the distance between the center O3 of the first slider 40 and the axis O0 of the first segment 121 is equal to the eccentricity of the eccentric portion 11 on the first segment 121, and the eccentricity of the first segment 121 is equal to the distance between the axis O0 of the first segment 121 and the axis O1' of the first cross-groove segment 33. The eccentric distance between the two segments is such that the first segment 121 rotates to drive the first slider 40 to make a circular motion, and the first slider 40 interacts with the first cross groove segment 33 and slides back and forth in the limiting channel 31 of the first cross groove segment 33; the second slider 40 makes a circular motion with the axis O0' of the second segment 122 as the center, and the distance between the center O4 of the second slider 40 and the axis O0' of the second segment 122 is equal to the eccentricity of the eccentric part 11 on the second segment 122, and the eccentricity of the second segment 122 is equal to the eccentric distance between the axis O0' of the second segment 122 and the axis O1' of the second cross groove segment 34. The second segment 122 rotates to drive the second slider 40 to make a circular motion, and the second slider 40 interacts with the second cross groove segment 34 and slides back and forth in the limiting channel 31 of the second cross groove segment 34.

[0233] The fluid machinery operating under the second operating method described above constitutes a cross-slider mechanism. This operating method adopts the principle of a cross-slider mechanism, wherein the eccentric part 11 on the first segment 121 serves as the first connecting rod L1, the eccentric part 11 on the second segment 122 serves as the second connecting rod L2, the limiting channel 31 of the first cross groove segment 33 serves as the third connecting rod L3, and the limiting channel 31 of the second cross groove segment 34 serves as the fourth connecting rod L4. The lengths of the first connecting rod L1 and the second connecting rod L2 are equal (please refer to...). Figure 29 ).

[0234] like Figure 29 As shown, there is a first included angle A between the first link L1 and the second link L2, and a second included angle B between the third link L3 and the fourth link L4, wherein the first included angle A is twice the second included angle B.

[0235] like Figure 30As shown, the line connecting the axis O0 of the first segment 121, the axis O0' of the second segment 122, the axis O1 of the first cross groove segment 33, and the axis O1' of the second cross groove segment 34 is the connecting line O0 O0'O1 O1'. The first connecting rod L1 has a third included angle C with the connecting line O0 O0'O1 O1', and the corresponding third connecting rod L3 has a fourth included angle D with the connecting line O0 O0'O1 O1', wherein the third included angle C is twice the fourth included angle D; the second connecting rod L2 has a fifth included angle E with the connecting line O0 O0'O1 O1', and the corresponding fourth connecting rod L4 has a sixth included angle F with the connecting line O0 O0'O1 O1', wherein the fifth included 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, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

[0236] Furthermore, the operating method also includes the fact that the rotational angular velocity of the slider 40 is the same as the revolution angular velocity of the slider 40; and the revolution angular velocity of the first cross groove segment 33 and the second cross groove segment 34 is the same as the rotational angular velocity of the slider 40.

[0237] Specifically, the axis O0 of the first segment 121 corresponds to the rotation center of the first connecting rod L1, the axis O0' of the second segment 122 corresponds to the rotation center of the second connecting rod L2, the axis O1 of the first cross-groove segment 33 corresponds to the rotation center of the third connecting rod L3, and the axis O1' of the second cross-groove segment 34 corresponds to the rotation center of the fourth connecting rod L4. The two eccentric parts 11 of the crankshaft 10 serve as the first connecting rod L1 and the second connecting rod L2, respectively, and the two limiting channels 31 of the cross-groove structure 30 serve as the third connecting rod L3 and the fourth connecting rod L4, respectively. The lengths of the first connecting rod L1 and the second connecting rod L2 are equal. Thus, while the crankshaft 10 rotates, the eccentric parts 11 on the crankshaft 10 drive the corresponding slider 40 to revolve around the axis O0 of the first segment 121 and the axis O0' of the corresponding second segment 122. At the same time, the slider 40 can rotate relative to the eccentric parts 11, and the relative rotation of the two... With the same speed, the first slider 40 and the second slider 40 reciprocate within their respective limiting channels 31, driving the cross groove structure 30 to perform circular motion. Due to the limitation of the two limiting channels 31 of the cross groove structure 30, the movement directions of the two sliders 40 always have a phase difference of the second included angle B. When one of the two sliders 40 is at a dead point, the eccentric part 11 used to drive the other slider 40 has the maximum driving torque. The eccentric part 11 with the maximum driving torque can normally drive the corresponding slider 40 to rotate, thereby driving the cross groove structure 30 to rotate through the slider 40, and then driving the slider 40 at the dead point to continue rotating through the cross groove structure 30. This achieves stable operation of the fluid machinery, avoids the dead point position of the motion mechanism, improves the motion reliability of the fluid machinery, and thus ensures the working reliability of the heat exchange equipment.

[0238] It should be noted that, in this application, the maximum lever arm of the driving torque of the eccentric part 11 is 2e.

[0239] Under this motion method, the running trajectory of each slider 40 is a circle. One circle is centered on the axis O0 of the first segment 121 and has the line O0O1' as its radius. The other circle is centered on the axis O0' of the second segment 122 and has the line O0'O1 as its radius.

[0240] It should be noted that in this application, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 revolutions, completing 4 intake and exhaust processes.

[0241] Two alternative implementation methods will be given below to provide a detailed description of the structure of the fluid machinery, so as to better illustrate the operation method of the fluid machinery through structural features.

[0242] like Figure 33 , Figure 34 , Figure 35 , Figures 37 to 42 As shown, the crankshaft 10's shaft portion 12 includes a first section 121 and a second section 122 connected axially thereto. The first section 121 and the second section 122 are coaxially disposed and movably connected. Two eccentric portions 11 are respectively disposed on the first section 121 and the second section 122. This ensures the construction... Figure 29 The organizations within the organization are able to operate normally.

[0243] like Figure 33 , Figure 34 , Figure 35 , Figures 37 to 42 As shown, the crankshaft 10 also includes a sliding connector 13. The first segment 121 is movably connected to the second segment 122 via the sliding connector 13. When the first segment 121 rotates, the sliding connector 13 slides relative to the first segment 121, and when the second segment 122 rotates, the sliding connector 13 slides relative to the second segment 122. This ensures the reliability of the connection between the first segment 121 and the second segment 122, as well as the reliability of the rotation of the first segment 121 and the second segment 122.

[0244] like Figure 35 , Figure 36 , Figures 38 to 42As shown, the sliding connector 13 has two limiting grooves 131, both of which extend perpendicularly to the axial direction of the crankshaft 10, and their extension directions are perpendicular to each other. The end of the first segment 121 facing the sliding connector 13 has a first protrusion structure 1211, and the end of the second segment 122 facing the sliding connector 13 has a second protrusion structure 1221. The first protrusion structure 1211 and the second protrusion structure 1221 are slidably disposed within the two limiting grooves 131, respectively. The first segment 121 rotates to cause the first protrusion structure 1211 to... 1. While reciprocating within the corresponding limiting groove 131, the first segment 122 interacts with the sliding connector 13. The sliding connector 13 rotates, causing the second protruding structure 1221 to reciprocate within the corresponding limiting groove 131, while simultaneously driving the second segment 122 to rotate. Alternatively, the second segment 122 rotates so that the second protruding structure 1221 reciprocates within the corresponding limiting groove 131 while interacting with the sliding connector 13. The sliding connector 13 rotates, causing the first protruding structure 1211 to reciprocate within the corresponding limiting groove 131, while simultaneously driving the first segment 121 to rotate. This ensures the reliable connection between the first segment 121 and the second segment 122, as well as the reliable rotation of the first segment 121 and the second segment 122.

[0245] It should be noted that, in an embodiment not shown in this application, the sliding connector 13 has two limiting protrusions extending toward the first segment 121 and the second segment 122 respectively; the end of the first segment 121 facing the sliding connector 13 has a first groove structure, and the end of the second segment 122 facing the sliding connector 13 has a second groove structure. The two limiting protrusions are slidably disposed within the first groove structure and the second groove structure respectively, and the extension direction of the first groove structure is perpendicular to the extension direction of the second groove structure; while the first segment 121 rotates to make the corresponding limiting protrusion slide back and forth within the first groove structure, the first groove structure interacts with the sliding connector 13, and the sliding connector 13 rotates and drives the limiting protrusion to slide back and forth within the second groove structure while driving the second segment 122 to rotate; or, while the second segment 122 rotates to make the corresponding limiting protrusion slide back and forth within the second groove structure, the second groove structure interacts with the sliding connector 13, and the sliding connector 13 rotates and drives the limiting protrusion to slide back and forth within the first groove structure while driving the first segment 121 to rotate. This ensures the reliability of the connection between the first segment 121 and the second segment 122, as well as the reliability of the rotation of the first segment 121 and the second segment 122.

[0246] like Figures 39 to 45As shown, the eccentricities of the two eccentric portions 11 are equal. Specifically, the assembly eccentricity of the first segment 121 with its corresponding first cross groove segment 33 is equal to the eccentricity of the eccentric portion 11 on the first segment 121, and the assembly eccentricity of the second segment 122 with its corresponding second cross groove segment 34 is equal to the eccentricity of the eccentric portion 11 on the second segment 122. This ensures the construction... Figure 29 The motion mechanism in the middle can operate normally. The eccentricity of the eccentric part 11 on the first segment 121 is e1, and the eccentricity of the eccentric part 11 on the second segment 122 is e2. e1 is not equal to e2. Figure 44 and Figure 45 In the diagram, H1 represents the axis of the first segment 121, H2 represents the axis of the second segment 122, I represents the axis of the upper half of the inner ring of cylinder liner 20, and J represents the axis of the lower half of the inner ring of cylinder liner 20.

[0247] In the second implementation of this embodiment, as follows Figure 31 and Figure 32 As shown, the fluid machinery operating as described above constitutes a cross-slider mechanism. This operating method adopts the principle of the cross-slider mechanism. In this method, the eccentric part 11 on the first segment 121 serves as the first connecting rod L1, the eccentric part 11 on the second segment 122 serves as the second connecting rod L2, the limiting channel 31 of the first cross groove segment 33 serves as the third connecting rod L3, and the limiting channel 31 of the second cross groove segment 34 serves as the fourth connecting rod L4. The difference between this embodiment and the first embodiment is that the lengths of the first connecting rod L1 and the second connecting rod L2 are not equal.

[0248] It should be noted that in this embodiment, the eccentricities of the two eccentric portions 11 are not equal. Specifically, the assembly eccentricity of the first segment 121 and its corresponding first cross groove segment 33 is equal to the eccentricity of the eccentric portion 11 on the first segment 121, and the assembly eccentricity of the second cross groove segment 34 corresponding to the second segment 122 is equal to the eccentricity of the eccentric portion 11 on the second segment 122. This ensures the construction... Figure 31 The motion mechanism within is functioning normally.

[0249] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0250] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0251] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0252] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0253] It should be noted that the terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in sequences other than those illustrated or described herein.

[0254] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A fluid machine, characterized in that, include: A crankshaft (10) having two eccentric portions (11) arranged along its axial direction, the two eccentric portions (11) having a phase difference of a first included angle A; Cylinder liner (20), the crankshaft (10) and the cylinder liner (20) are eccentrically arranged and the eccentric distance is fixed; A cross-groove structure (30) is rotatably disposed within the cylinder liner (20). The cross-groove structure (30) includes a first cross-groove segment (33) and a second cross-groove segment (34) connected along its axial direction. The first cross-groove segment (33) and the second cross-groove segment (34) are coaxially disposed and movably connected. Both the first cross-groove segment (33) and the second cross-groove segment (34) have limiting channels (31). The 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 there is a phase difference of a second included angle B between the extending directions of the two limiting channels (31). 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). The two eccentric parts (11) extend into the two through holes (41) of the two sliders (40). The two sliders (40) are slidably disposed 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) while interacting with the cross groove structure (30), so that the cross groove structure (30) and the slider (40) rotate in the cylinder liner (20).

2. The fluid machinery according to claim 1, characterized in that, The distance between the inner ring axis of the cylinder liner (20) located at the first cross groove section (33) and the inner ring axis of the cylinder liner (20) located at the second cross groove section (34) is equal to the eccentric distance between the first cross groove section (33) and the second cross groove section (34).

3. The fluid machinery according to claim 1, characterized in that, The cross groove structure (30) further includes a first sliding connector (35). The first cross groove segment (33) is movably connected to the second cross groove segment (34) through the first sliding connector (35). When the first cross groove segment (33) rotates, the first sliding connector (35) slides relative to the first cross groove segment (33). When the second cross groove segment (34) rotates, the first sliding connector (35) slides relative to the second cross groove segment (34).

4. The fluid machinery according to claim 3, characterized in that, The first sliding connector (35) has two first limiting grooves (351), the extension direction of the two first limiting grooves (351) is perpendicular to the axial direction of the crankshaft (10), and the extension directions of the two first limiting grooves (351) are perpendicular to each other. The first cross groove segment (33) has a third protrusion structure (331) at the end facing the first sliding connector (35), and the second cross groove segment (34) has a fourth protrusion structure (341) at the end facing the first sliding connector (35). The third protrusion structure (331) and the fourth protrusion structure (341) are respectively slidably disposed in the two first limiting grooves (351). The first cross groove segment (33) rotates to allow the third protruding structure (331) to reciprocate within the corresponding first limiting groove (351) while interacting with the first sliding connector (35). The first sliding connector (35) rotates and drives the fourth protruding structure (341) to reciprocate within the corresponding first limiting groove (351) while simultaneously driving the second cross groove segment (34) to rotate; or, The second cross groove segment (34) rotates so that the fourth protrusion structure (341) slides back and forth in the corresponding first limiting slide groove (351) while interacting with the first sliding connector (35). The first sliding connector (35) rotates and drives the third protrusion structure (331) to slide back and forth in the corresponding first limiting slide groove (351) while driving the first cross groove segment (33) to rotate.

5. The fluid machinery according to claim 3, characterized in that, The first sliding connector (35) has two first limiting protrusions extending toward the first cross groove segment (33) and the second cross groove segment (34), respectively; The first cross groove segment (33) has a third groove structure at the end facing the first sliding connector (35), and the second cross groove segment (34) has a fourth groove structure at the end facing the first sliding connector (35). The two first limiting protrusions are respectively slidably disposed in the third groove structure and the fourth groove structure, and the extension direction of the third groove structure is perpendicular to the extension direction of the fourth groove structure. While the first cross groove segment (33) rotates to make the corresponding first limiting protrusion slide back and forth in the third slide groove structure, the third slide groove structure interacts with the first sliding connector (35). The first sliding connector (35) rotates and drives the first limiting protrusion to slide back and forth in the fourth slide groove structure, while driving the second cross groove segment (34) to rotate; or, As the second cross groove segment (34) rotates to make the corresponding first limiting protrusion slide back and forth in the fourth slide groove structure, the fourth slide groove structure interacts with the first sliding connector (35). The first sliding connector (35) rotates and drives the first limiting protrusion to slide back and forth in the third slide groove structure, while driving the first cross groove segment (33) to rotate.

6. The fluid machinery according to claim 1, characterized in that, The crankshaft (10) has a shaft portion (12) integrally formed, and the shaft portion (12) has only one shaft.

7. The fluid machinery according to claim 1, characterized in that, The crankshaft (10) includes a shaft portion (12) comprising a first section and a second section connected along its axial direction, the first section and the second section being coaxially arranged, and two eccentric portions (11) being respectively arranged on the first section and the second section.

8. The fluid machinery according to claim 7, characterized in that, The first segment and the second segment are detachably connected.

9. The fluid machinery according to claim 6 or 7, characterized in that, The eccentricities of the two eccentric portions (11) are not equal, wherein, The eccentricity of the first eccentric part (11) is equal to the assembly eccentricity of the crankshaft (10) and the corresponding first cross groove segment (33); The eccentricity of the second eccentric part (11) is equal to the assembly eccentricity of the crankshaft (10) and the corresponding second cross groove section (34).

10. The fluid machinery according to claim 1, characterized in that, The crankshaft (10) includes a shaft portion (12) comprising a first section (121) and a second section (122) connected along its axial direction. The first section (121) and the second section (122) are coaxially disposed and movably connected. Two eccentric portions (11) are respectively disposed on the first section (121) and the second section (122).

11. The fluid machinery according to claim 10, characterized in that, The crankshaft (10) further includes a sliding connector (13). The first segment (121) is movably connected to the second segment (122) through the sliding connector (13). While the first segment (121) rotates, the sliding connector (13) slides relative to the first segment (121). While the second segment (122) rotates, the sliding connector (13) slides relative to the second segment (122).

12. The fluid machinery according to claim 11, characterized in that, The sliding connector (13) has two limiting grooves (131), the extension directions of the two limiting grooves (131) are perpendicular to the axial direction of the crankshaft (10), and the extension directions of the two limiting grooves (131) are perpendicular to each other. The first segment (121) has a first protrusion structure (1211) at the end facing the sliding connector (13), and the second segment (122) has a second protrusion structure (1221) at the end facing the sliding connector (13). The first protrusion structure (1211) and the second protrusion structure (1221) are respectively slidably disposed in two limiting grooves (131). The first segment (121) rotates to allow the first protruding structure (1211) to reciprocate within the corresponding limiting groove (131) while interacting with the sliding connector (13). The sliding connector (13) rotates and drives the second protruding structure (1221) to reciprocate within the corresponding limiting groove (131), while simultaneously driving the second segment (122) to rotate; or, The second segment (122) rotates so that the second protruding structure (1221) slides back and forth in the corresponding limiting groove (131) while interacting with the sliding connector (13). The sliding connector (13) rotates and drives the first protruding structure (1211) to slide back and forth in the corresponding limiting groove (131) while driving the first segment (121) to rotate.

13. The fluid machinery according to claim 11, characterized in that, The sliding connector (13) has two limiting protrusions extending toward the first segment (121) and the second segment (122) respectively; The end of the first segment (121) facing the sliding connector (13) has a first groove structure, and the end of the second segment (122) facing the sliding connector (13) has a second groove structure. The two limiting protrusions are respectively slidably disposed in the first groove structure and the second groove structure, and the extension direction of the first groove structure is perpendicular to the extension direction of the second groove structure. While the first segment (121) rotates to make the corresponding limiting protrusion slide back and forth in the first slide groove structure, the first slide groove structure interacts with the sliding connector (13). The sliding connector (13) rotates and drives the limiting protrusion to slide back and forth in the second slide groove structure, while driving the second segment (122) to rotate; or, As the second segment (122) rotates to make the corresponding limiting protrusion slide back and forth in the second slide groove structure, the second slide groove structure interacts with the sliding connector (13). The sliding connector (13) rotates and drives the limiting protrusion to slide back and forth in the first slide groove structure, while driving the first segment (121) to rotate.

14. The fluid machinery according to claim 10, characterized in that, The eccentricities of the two eccentric portions (11) are equal, wherein, The assembly eccentricity of the first segment (121) and the corresponding first cross groove segment (33) is equal to the eccentricity of the eccentric part (11) provided on the first segment (121), and the assembly eccentricity of the second segment (122) and the corresponding second cross groove segment (34) is equal to the eccentricity of the eccentric part (11) provided on the second segment (122).

15. The fluid machinery according to claim 10, characterized in that, The eccentricities of the two eccentric portions (11) are not equal, wherein, The assembly eccentricity of the first segment (121) and the corresponding first cross groove segment (33) is equal to the eccentricity of the eccentric part (11) provided on the first segment (121), and the assembly eccentricity of the second cross groove segment (34) corresponding to the second segment (122) is equal to the eccentricity of the eccentric part (11) provided on the second segment (122).

16. The fluid machinery according to claim 1, characterized in that, The shaft portion (12) of the crankshaft (10) is integrally formed with the eccentric portion (11); or, The shaft portion (12) of the crankshaft (10) is detachably connected to the eccentric portion (11).

17. The fluid machinery according to claim 1, characterized in that, One of the two limiting channels (31) extends to the outer periphery of the first cross groove segment (33) at both ends, and the other of the two limiting channels (31) extends to the outer periphery of the second cross groove segment (34) at both ends.

18. The fluid machinery according to claim 1, characterized in that, The two sliders (40) are respectively concentrically arranged with the two eccentric parts (11). The sliders (40) move in a circular motion around the axis of the crankshaft (10) of the eccentric part (11). There is a first rotation gap between the hole wall of the through hole (41) and the eccentric part (11). The range of the first rotation gap is 0.005mm to 0.05mm.

19. The fluid machinery according to claim 1, characterized in that, There is a second rotational clearance between the outer peripheral surface of the first cross groove section (33) and the inner wall surface of one axial end of the cylinder liner (20), the second rotational clearance being in the range of 0.01mm to 0.08mm. There is a third rotational clearance between the outer peripheral surface of the second cross groove section (34) and the inner wall surface of the other axial end of the cylinder liner (20), the third rotational clearance being in the range of 0.01mm to 0.08mm.

20. The fluid machinery according to claim 1, characterized in that, The first included angle A is 160 degrees to 200 degrees; the second included angle B is 80 degrees to 100 degrees.

21. The fluid machinery according to claim 1, characterized in that, The fluid machinery also includes a flange (50) disposed at the axial end of the cylinder liner (20), and the crankshaft (10) is concentrically disposed with the flange (50).

22. The fluid machinery according to claim 21, characterized in that, There is a first assembly gap between the crankshaft (10) and the flange (50), the first assembly gap being in the range of 0.005mm to 0.05mm.

23. The fluid machinery according to claim 22, characterized in that, The first assembly gap ranges from 0.01 to 0.03 mm.

24. The fluid machinery according to claim 1, characterized in that, The eccentric part (11) has an arc surface, and the central angle of the arc surface is greater than or equal to 180 degrees.

25. The fluid machinery according to claim 1, characterized in that, The eccentric part (11) is cylindrical.

26. The fluid machinery according to claim 25, characterized in that, The proximal end of the eccentric portion (11) is flush with the outer circle of the shaft portion (12) of the crankshaft (10); or, The proximal end of the eccentric portion (11) protrudes beyond the outer circle of the shaft portion (12) of the crankshaft (10); or, The proximal end of the eccentric portion (11) is located inside the outer circle of the shaft portion (12) of the crankshaft (10).

27. The fluid machinery according to claim 1, characterized in that, The slider (40) includes multiple substructures, which are spliced ​​together to form the through hole (41).

28. The fluid machinery according to claim 1, characterized in that, The two eccentric portions (11) are spaced apart axially on the crankshaft (10).

29. The fluid machinery according to claim 1, characterized in that, Both the first cross groove segment (33) and the second cross groove segment (34) have a center hole (32). The two center holes (32) are not concentrically arranged, and the two limiting channels (31) are connected through the two center holes (32). The diameter of each center hole (32) is larger than the diameter of the shaft portion (12) of the crankshaft (10).

30. The fluid machinery according to claim 29, characterized in that, The diameter of the central hole (32) is larger than the diameter of the eccentric part (11).

31. The fluid machinery according to claim 1, characterized in that, The slider (40) has two relatively parallel straight line segments and an arc segment connecting the ends of the two straight line segments in the axial projection of the through hole (41).

32. The fluid machinery according to claim 1, characterized in that, The limiting channel (31) has a set of opposing first sliding surfaces that slide in 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 pressing surface (42) facing the end of the limiting channel (31). The pressing surface (42) serves as the head of the slider (40). The two second sliding surfaces are connected through the pressing surface (42). The pressing surface (42) faces the variable volume cavity (311).

33. The fluid machinery according to claim 32, characterized in that, The extrusion surface (42) is an arc surface, and the distance between the center of the arc surface and the center of the through hole (41) is equal to the eccentricity of the eccentric part (11).

34. The fluid machinery according to claim 33, characterized in that, The radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner (20); or, The radius of curvature of the arc surface has a difference from the radius of the inner circle of the cylinder liner (20), and the difference ranges from -0.05mm to 0.025mm.

35. The fluid machinery according to claim 34, characterized in that, The difference ranges from -0.02 to 0.02 mm.

36. The fluid machinery according to claim 32, characterized in that, The projected area S of the extrusion surface (42) in the sliding direction of the slider (40) 滑块 The area of ​​the compression exhaust port of the cylinder liner (20) is S 排 The following conditions must be met between them: S 滑块 / S 排 The value is 8 to 25.

37. The fluid machinery according to claim 36, characterized in that, S 滑块 / S 排 The value is 12 to 18.

38. The fluid machinery according to claim 1, characterized in that, The cylinder liner (20) has a compression inlet (21) and a compression exhaust outlet (22). When any of the sliders (40) is in the air intake position, the compression air intake (21) is connected to the corresponding variable volume cavity (311); When any of the sliders (40) is in the exhaust position, the corresponding variable volume chamber (311) is connected to the compression exhaust port (22).

39. The fluid machinery according to claim 38, characterized in that, The inner wall of the cylinder liner (20) has an intake chamber (23), which is connected to the compression inlet (21).

40. The fluid machinery according to claim 39, characterized in that, The intake chamber (23) extends circumferentially around the inner wall of the cylinder liner (20) by a first preset distance to form an arc-shaped intake chamber (23).

41. The fluid machinery according to claim 39, characterized in that, There are two intake chambers (23), which are spaced apart along the axial direction of the cylinder liner (20). The cylinder liner (20) also has an intake communication chamber (24). Both intake chambers (23) are connected to the intake communication chamber (24), and the compression inlet (21) is connected to the intake chamber (23) through the intake communication chamber (24).

42. The fluid machinery according to claim 41, characterized in that, The intake communication cavity (24) extends a second preset distance along the axial direction of the cylinder liner (20), and at least one end of the intake communication cavity (24) penetrates the axial end face of the cylinder liner (20).

43. The fluid machinery according to claim 38, characterized in that, An exhaust chamber (25) is provided on the outer wall of the cylinder liner (20), and the compression exhaust port (22) is connected to the exhaust chamber (25) through the inner wall of the cylinder liner (20). The fluid machinery also includes an exhaust valve assembly (60), which is disposed in the exhaust chamber (25) and corresponds to the compression exhaust port (22).

44. The fluid machinery according to claim 43, characterized in that, There are two compression exhaust ports (22), which are spaced apart along the axial direction of the cylinder liner (20). There are two sets of exhaust valve assemblies (60), which are respectively set to correspond to the two compression exhaust ports (22).

45. The fluid machinery according to claim 44, characterized in that, The cylinder liner (20) is also provided with a connecting hole (26) on its axial end face. The connecting hole (26) is connected to the exhaust chamber (25). The fluid machinery also includes a flange (50). The flange (50) is provided with an exhaust passage (51). The connecting hole (26) is connected to the exhaust passage (51).

46. ​​The fluid machinery according to claim 43, characterized in that, The exhaust chamber (25) extends to the outer wall of the cylinder liner (20), and the fluid machinery also includes an exhaust cover plate (70), which is connected to the cylinder liner (20) and seals the exhaust chamber (25).

47. The fluid machinery according to any one of claims 38 to 46, characterized in that, The fluid machinery in question is a compressor.

48. The fluid machinery according to claim 1, characterized in that, The cylinder liner (20) has an expansion exhaust port and an expansion intake port. When any of the sliders (40) is in the air intake position, the expansion exhaust port is connected to the corresponding variable volume cavity (311); When any of the sliders (40) is in the exhaust position, the corresponding variable volume chamber (311) is connected to the expansion inlet.

49. The fluid machinery according to claim 48, characterized in that, The inner wall surface of the cylinder liner (20) has an expansion exhaust chamber (25), which is connected to the expansion exhaust port.

50. The fluid machinery according to claim 49, characterized in that, The expansion exhaust chamber extends circumferentially around the inner wall of the cylinder liner (20) by a first preset distance to form an arc-shaped expansion exhaust chamber. The expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion intake port is located. The extension direction of the expansion exhaust chamber is in the same direction as the rotation direction of the cross groove structure (30).

51. The fluid machinery according to claim 50, characterized in that, There are two expansion exhaust chambers, which are spaced apart along the axial direction of the cylinder liner (20). The cylinder liner (20) also has an expansion exhaust communication chamber. Both expansion exhaust chambers are connected to the expansion exhaust communication chamber, and the expansion exhaust port is connected to the expansion exhaust chamber through the expansion exhaust communication chamber.

52. The fluid machinery according to claim 51, characterized in that, The expansion exhaust communication cavity extends along the axial direction of the cylinder liner (20) by a second predetermined distance, and at least one end of the expansion exhaust communication cavity penetrates the axial end face of the cylinder liner (20).

53. The fluid machinery according to any one of claims 48 to 52, characterized in that, The fluid machinery in question is an expander.

54. A heat exchange device, comprising fluid machinery, characterized in that, The fluid machinery is the fluid machinery according to any one of claims 1 to 53.

55. A method for operating fluid machinery, characterized in that, include: The crankshaft (10) rotates about its axis O0; The first cross groove segment (33) revolves around the axis O0 of the crankshaft (10), and the axis O0 of the crankshaft (10) is eccentrically set with the axis O1 of the first cross groove segment (33) and the eccentric distance is fixed. The second cross groove segment (34) revolves around the axis O0 of the crankshaft (10), and the axis O0 of the crankshaft (10) is eccentrically set with the axis O1' of the second cross groove segment (34) and the eccentric distance is fixed. The first slider (40) moves in a circle with the axis O0 of the crankshaft (10) as the center. The distance between the center O3 of the first slider (40) and the axis O0 of the crankshaft (10) is equal to the eccentricity of the first eccentric part (11) of the crankshaft (10). The eccentricity is equal to the eccentric distance between the axis O0 of the crankshaft (10) and the axis O1 of the first cross groove segment (33). The crankshaft (10) rotates to drive the first slider (40) to move in a circle. The first slider (40) interacts with the first cross groove segment (33) and slides back and forth in the limiting channel (31) of the first cross groove segment (33). The second slider (40) moves in a circular motion with the axis O0 of the crankshaft (10) as the center. The distance between the center O4 of the second slider (40) and the axis O0 of the crankshaft (10) is equal to the eccentricity of the second eccentric part (11) corresponding to the crankshaft (10). The eccentricity is equal to the eccentric distance between the axis O0 of the crankshaft (10) and the axis O1' of the second cross groove segment (34). The crankshaft (10) rotates to drive the second slider (40) to move in a circular motion. The second slider (40) interacts with the second cross groove segment (34) and slides back and forth in the limiting channel (31) of the second cross groove segment (34).

56. The operating method according to claim 55, characterized in that, The operating method adopts the principle of cross-slider mechanism, wherein the two eccentric parts (11) of the crankshaft (10) serve as the first connecting rod L1 and the second connecting rod L2 respectively, the limiting channel (31) of the first cross groove section (33) serves as the third connecting rod L3, and the limiting channel (31) of the second cross groove section (34) serves as the fourth connecting rod L4, wherein the lengths of the first connecting rod L1 and the second connecting rod L2 are not equal.

57. The operating method according to claim 56, characterized in that, The first link L1 and the second link L2 have a first included angle A, and the third link L3 and the fourth link L4 have a second included angle B, wherein the first included angle A is twice the second included angle B.

58. The operating method according to claim 57, characterized in that, The line connecting the crankshaft (10) axis center O0, the first cross groove segment (33) axis center O1, and the second cross groove segment (34) axis center O1' is the connecting line O0O1O1'. The first link L1 has a third included angle C with the connecting line O0O1O1', and the corresponding third link L3 has a fourth included angle D with the connecting line O0O1O1', wherein the third included angle C is twice the fourth included angle D; The second link L2 has a fifth included angle E with the connecting line O0O1O1', and the corresponding fourth link L4 has a sixth included angle F with the connecting line O0O1O1', wherein the fifth included 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, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

59. The operating method according to claim 55, characterized in that, The operating method further includes: The rotational angular velocity of the slider (40) is the same as the revolution angular velocity of the slider (40); The revolution angular velocity of the first cross groove segment (33) and the second cross groove segment (34) is the same as the rotation angular velocity of the slider (40).

60. The operating method according to claim 55, characterized in that, During the rotation of the crankshaft (10), the crankshaft (10) rotates 2 revolutions, completing 4 intake and exhaust processes.

61. The operating method according to claim 55, characterized in that, include: The first segment (121) of the crankshaft (10) rotates around the axis O0 of the first segment (121), and the second segment (122) of the crankshaft (10) rotates around the axis O0' of the second segment (122), wherein O0 and O0' do not coincide; The axis O0 of the first segment (121) is eccentrically set with the axis O1 of the first cross groove segment (33) and the eccentric distance is fixed; the axis O0' of the second segment (122) is eccentrically set with the axis O1' of the second cross groove segment (34) and the eccentric distance is fixed. The first slider (40) moves in a circle around the axis O0 of the first segment (121), and the distance between the center O3 of the first slider (40) and the axis O0 of the first segment (121) is equal to the eccentricity of the eccentric part (11) on the first segment (121), and the eccentricity of the first segment (121) is equal to the eccentric distance between the axis O0 of the first segment (121) and the axis O1 of the first cross groove segment (33). The first segment (121) rotates to drive the first slider (40) to move in a circle, and the first slider (40) interacts with the first cross groove segment (33) and slides back and forth in the limiting channel (31) of the first cross groove segment (33). The second slider (40) moves in a circle around the axis O0' of the second segment (122), and the distance between the center O4 of the second slider (40) and the axis O0' of the second segment (122) is equal to the eccentricity of the eccentric part (11) on the second segment (122), and the eccentricity of the second segment (122) is equal to the eccentric distance between the axis O0' of the second segment (122) and the axis O1' of the second cross groove segment (34). The second segment (122) rotates to drive the second slider (40) to move in a circle, and the second slider (40) interacts with the second cross groove segment (34) and slides back and forth in the limiting channel (31) of the second cross groove segment (34).

62. The operating method according to claim 61, characterized in that, The operating method adopts the principle of a cross slider mechanism, wherein the eccentric part (11) on the first segment (121) serves as the first connecting rod L1, the eccentric part (11) on the second segment (122) serves as the second connecting rod L2, the limiting channel (31) of the first cross groove segment (33) serves as the third connecting rod L3, and the limiting channel (31) of the second cross groove segment (34) serves as the fourth connecting rod L4, wherein the lengths of the first connecting rod L1 and the second connecting rod L2 are equal.

63. The operating method according to claim 61, characterized in that, The operating method adopts the principle of a cross-slider mechanism, wherein the eccentric part (11) on the first segment (121) serves as the first connecting rod L1, the eccentric part (11) on the second segment (122) serves as the second connecting rod L2, the limiting channel (31) of the first cross groove segment (33) serves as the third connecting rod L3, and the limiting channel (31) of the second cross groove segment (34) serves as the fourth connecting rod L4, wherein the lengths of the first connecting rod L1 and the second connecting rod L2 are not equal.

64. The operating method according to claim 62 or 63, characterized in that, The first link L1 and the second link L2 have a first included angle A, and the third link L3 and the fourth link L4 have a second included angle B, wherein the first included angle A is twice the second included angle B.

65. The operating method according to claim 64, characterized in that, The line connecting the axis O0 of the first segment (121), the axis O0' of the second segment (122), the axis O1 of the first cross groove segment (33), and the axis O1' of the second cross groove segment (34) is line O0O0'O1O1'. The first link L1 has a third included angle C with the connecting line O0O0'O1O1', and the corresponding third link L3 has a fourth included angle D with the connecting line O0O0'O1O1', wherein the third included angle C is twice the fourth included angle D; The second link L2 has a fifth included angle E with the line O0O0'O1O1', and the corresponding fourth link L4 has a sixth included angle F with the line O0O0'O1O1', wherein the fifth included 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, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

66. The operating method according to claim 61, characterized in that, The operating method further includes: The rotational angular velocity of the slider (40) is the same as the revolution angular velocity of the slider (40); The revolution angular velocity of the first cross groove segment (33) and the second cross groove segment (34) is the same as the rotation angular velocity of the slider (40).

67. The operating method according to claim 61, characterized in that, During the rotation of the crankshaft (10), the crankshaft (10) rotates 2 revolutions, completing 4 intake and exhaust processes.

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