Fluid machine, heat exchange device, and method for operating a fluid machine

Abstract

The application provides a fluid machine, a heat exchange device and a running method of the fluid machine, and the fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure and a sliding block, the crankshaft has a first included angle A between two eccentric parts, and the eccentric amounts of the two eccentric parts are not equal; the crankshaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve, two limiting channels of the cross groove structure are sequentially arranged along the axial direction of the crankshaft, the extension direction of the limiting channel is perpendicular to the axial direction of the crankshaft, and the extension directions of the two limiting channels have a second included angle B, the first included angle A is twice the second included angle B; the two eccentric parts correspondingly extend into two through holes of the two sliding blocks, and the two sliding blocks are correspondingly arranged in the two limiting channels and form a variable volume cavity. The application solves the problems of low energy efficiency and large noise of the compressor in the prior art.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heat exchange systems, in particular to a fluid machine, a heat exchange device and a method for operating the fluid machine. BACKGROUND

[0002] The fluid machine in the prior art includes compressors and expanders, etc. Taking the compressor as an example.

[0003] According to the national energy conservation and environmental protection policy and the comfort requirement of consumers for air conditioners, the air conditioning industry has been pursuing high efficiency and low noise. The compressor, as the heart of the air conditioner, has a direct impact on the energy efficiency and noise level of the air conditioner. The rolling rotor compressor, as the mainstream household air conditioner compressor, has been relatively mature after nearly a hundred years of development. The optimization space is limited due to the structural principle. If a major breakthrough is to be made, innovation is needed from the structural principle.

[0004] Therefore, there is an urgent need to provide a compressor with high energy efficiency and low noise. SUMMARY

[0005] The main purpose of the present application 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 large noise of the compressor in the prior art.

[0006] In order to achieve the above-mentioned purpose, according to one aspect of the present application, a fluid machine includes a crankshaft, a cylinder sleeve, a cross groove structure and a slider, wherein the crankshaft is provided with two eccentric parts along its axial direction, the two eccentric parts have a phase difference of a first included angle A, and the eccentric amounts of the two eccentric parts are not equal; the crankshaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve, the cross groove structure has two limiting channels, the two limiting channels are sequentially arranged along the axial direction of the crankshaft, the extension direction of the limiting channel is perpendicular to the axial direction of the crankshaft, and the extension directions of the two limiting channels have a phase difference of a second included angle B, wherein 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 correspondingly extend into the two through holes of the two sliders, the two sliders are correspondingly 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, and the crankshaft rotates to drive the slider to reciprocally slide in the limiting channel while interacting with the cross groove structure, so that the cross groove structure and the slider rotate in the cylinder sleeve.

[0007] Further, the shaft body part of the crankshaft includes a first segment and a second segment connected along its axial direction, the first segment and the second segment are arranged in different axes and are movably connected, and the two eccentric parts are arranged on the first segment and the second segment respectively.

[0008] Further, the crankshaft further comprises a sliding connecting piece, the first section is movably connected with the second section through the sliding connecting piece, the first section rotates while the sliding connecting piece slides relative to the first section, and the second section rotates while the sliding connecting piece slides relative to the second section.

[0009] Further, the sliding connecting piece has two limiting sliding grooves, the extending directions of the two limiting sliding grooves are both perpendicular to the axial direction of the crankshaft, and the extending directions of the two limiting sliding grooves are perpendicular to each other; the end of the first section towards the side of the sliding connecting piece has a first protruding structure, the end of the second section towards the side of the sliding connecting piece has a second protruding structure, and the first protruding structure and the second protruding structure are respectively slidably arranged in the two limiting sliding grooves; the first section rotates to make the first protruding structure reciprocally slide in the corresponding limiting sliding groove while interacting with the sliding connecting piece, the sliding connecting piece rotates to drive the second protruding structure reciprocally slide in the corresponding limiting sliding groove while driving the second section to rotate; or, the second section rotates to make the second protruding structure reciprocally slide in the corresponding limiting sliding groove while interacting with the sliding connecting piece, the sliding connecting piece rotates to drive the first protruding structure reciprocally slide in the corresponding limiting sliding groove while driving the first section to rotate.

[0010] Further, the sliding connecting piece has two limiting protrusions respectively extending towards the first section and the second section; the end of the first section towards the side of the sliding connecting piece has a first sliding groove structure, the end of the second section towards the side of the sliding connecting piece has a second sliding groove structure, the two limiting protrusions are respectively slidably arranged in the first sliding groove structure and the second sliding groove structure, and the extending direction of the first sliding groove structure is perpendicular to the extending direction of the second sliding groove structure; the first section rotates to make the corresponding limiting protrusion reciprocally slide in the first sliding groove structure while the first sliding groove structure interacts with the sliding connecting piece, the sliding connecting piece rotates to drive the limiting protrusion reciprocally slide in the second sliding groove structure while driving the second section to rotate; or, the second section rotates to make the corresponding limiting protrusion reciprocally slide in the second sliding groove structure while the second sliding groove structure interacts with the sliding connecting piece, the sliding connecting piece rotates to drive the limiting protrusion reciprocally slide in the first sliding groove structure while driving the first section to rotate.

[0011] Further, the assembly eccentricity of the first section and the cylinder sleeve is equal to the eccentricity of the eccentric part arranged on the first section, and the assembly eccentricity of the second section and the cylinder sleeve is equal to the eccentricity of the eccentric part arranged on the second section.

[0012] Further, the two ends of the limiting channel pass through to the outer circumferential surface of the cross groove structure.

[0013] Further, the two sliding blocks are concentrically arranged with the two eccentric parts, the sliding blocks make circular motion around the shaft center of the crankshaft, the hole wall of the through hole and the eccentric part have a first rotation gap, and the range of the first rotation gap is 0.005mm-0.05mm.

[0014] Further, the cross groove structure is coaxially arranged with the cylinder sleeve, and a second rotation gap is formed between the outer circumferential surface of the cross groove structure and the inner wall surface of the cylinder sleeve, and the size of the second rotation gap is 0.005mm-0.1mm.

[0015] Further, the first included angle A is 160-200 degrees, and the second included angle B is 80-100 degrees.

[0016] Further, the fluid machine further comprises a flange, the flange is arranged at the axial end of the cylinder sleeve, and the crankshaft is coaxially arranged with the flange.

[0017] Further, a first assembly gap is formed between the crankshaft and the flange, and the size of the first assembly gap is 0.005mm-0.05mm.

[0018] Further, the size of the first assembly gap is 0.01-0.03mm.

[0019] Further, the eccentric part has a circular arc surface, and the central angle of the circular arc surface is greater than or equal to 180 degrees.

[0020] Further, the eccentric part is cylindrical.

[0021] Further, the proximal end of the eccentric part is flush with the outer circle of the shaft body part of the crankshaft, or the proximal end of the eccentric part protrudes from the outer circle of the shaft body part of the crankshaft, or the proximal end of the eccentric part is located on the inner side of the outer circle of the shaft body part of the crankshaft.

[0022] Further, the sliding block comprises a plurality of sub-structures, and the plurality of sub-structures are spliced to form a through hole.

[0023] Further, the two eccentric parts are arranged at intervals in the axial direction of the crankshaft.

[0024] Further, the cross groove structure has a central hole, and the two limiting channels are communicated through the central hole, and the hole diameter of the central hole is greater than the diameter of the shaft body part of the crankshaft.

[0025] Further, the hole diameter of the central hole is greater than the diameter of the eccentric part.

[0026] Further, the projection of the sliding block in the axial direction of the through hole has two opposite parallel straight line segments and an arc segment connecting the end portions of the two straight line segments.

[0027] Further, the limiting channel has a set of oppositely arranged first sliding surfaces in sliding contact with the sliding block, the sliding block has a second sliding surface matched with the first sliding surface, the sliding block has an extrusion surface towards the end portion of the limiting channel, the extrusion surface serves as the head of the sliding block, the two second sliding surfaces are connected through the extrusion surface, and the extrusion surface faces the variable volume cavity.

[0028] Further, the extrusion surface is an arc surface, and a distance between an arc center of the arc surface and a center of the through hole is equal to the eccentricity of the eccentric portion.

[0029] Further, a radius of curvature of the arc surface is equal to a radius of the inner circle of the cylinder liner, or the radius of curvature of the arc surface has a difference with the radius of the inner circle of the cylinder liner, and the difference ranges from -0.05 mm to 0.025 mm.

[0030] Further, the difference ranges from -0.02 mm to 0.02 mm.

[0031] Further, a projection area S 滑块 of the extrusion surface in a sliding direction of the sliding block satisfies the following relationship with an area S 排 of the compression exhaust port of the cylinder liner: S 滑块 / S 排 is 8-25.

[0032] Further, the value of S 滑块 / S 排 is 12-18.

[0033] Further, the cylinder liner has a compression intake port and a compression exhaust port, the compression intake port is communicated with the corresponding variable volume chamber when any sliding block is at an intake position, and the corresponding variable volume chamber is communicated with the compression exhaust port when any sliding block is at an exhaust position.

[0034] Further, an inner wall surface of the cylinder liner has a suction chamber, and the suction chamber is communicated with the compression intake port.

[0035] Further, the suction chamber extends a first preset distance along a circumferential direction of the inner wall surface of the cylinder liner to form an arc-shaped suction chamber.

[0036] Further, there are two suction chambers, the two suction chambers are arranged at intervals along an axial direction of the cylinder liner, the cylinder liner further has a suction communication chamber, the two suction chambers are both communicated with the suction communication chamber, and the compression intake port is communicated with the suction chambers through the suction communication chamber.

[0037] Further, the suction communication chamber extends a second preset distance along the axial direction of the cylinder liner, and at least one end of the suction communication chamber penetrates through an axial end surface of the cylinder liner.

[0038] Further, an exhaust chamber is formed in an outer wall of the cylinder liner, the compression exhaust port is communicated to the exhaust chamber from the inner wall of the cylinder liner, and the fluid machine further comprises an exhaust valve assembly arranged in the exhaust chamber and corresponding to the compression exhaust port.

[0039] Further, there are two compression exhaust ports, the two compression exhaust ports are arranged at intervals along the axial direction of the cylinder liner, and there are two groups of exhaust valve assemblies, the two groups of exhaust valve assemblies are respectively arranged corresponding to the two compression exhaust ports.

[0040] Further, the axial end surface of the cylinder sleeve is provided with a communication hole, the communication hole is communicated with the exhaust cavity, and the fluid machine further comprises a flange, the flange is provided with an exhaust passage, and the communication hole is communicated with the exhaust passage.

[0041] Further, the exhaust cavity penetrates to the outer wall surface of the cylinder sleeve, and the fluid machine further comprises an exhaust cover plate, the exhaust cover plate is connected with the cylinder sleeve and seals the exhaust cavity.

[0042] Further, the fluid machine is a compressor.

[0043] Further, the cylinder sleeve is provided with an expansion exhaust port and an expansion intake port, the expansion exhaust port is communicated with the corresponding variable volume cavity when any one of the sliding blocks is in the intake position, and the corresponding variable volume cavity is communicated with the expansion intake port when any one of the sliding blocks is in the exhaust position.

[0044] Further, the inner wall surface of the cylinder sleeve is provided with an expansion exhaust cavity, and the expansion exhaust cavity is communicated with the expansion exhaust port.

[0045] Further, the expansion exhaust cavity extends by a first preset distance along the circumference of the inner wall surface of the cylinder sleeve to form an arc-shaped expansion exhaust cavity, and the expansion exhaust cavity extends from the expansion exhaust port to the side where the expansion intake port is located, and the extension direction of the expansion exhaust cavity is the same as the rotation direction of the cross groove structure.

[0046] Further, the expansion exhaust cavity is two, the two expansion exhaust cavities are arranged in the axial direction of the cylinder sleeve, the cylinder sleeve is further provided with an expansion exhaust communication cavity, the two expansion exhaust cavities are both communicated with the expansion exhaust communication cavity, and the expansion exhaust port is communicated with the expansion exhaust cavity through the expansion exhaust communication cavity.

[0047] Further, the expansion exhaust communication cavity extends by a second preset distance in the axial direction of the cylinder sleeve, and at least one end of the expansion exhaust communication cavity penetrates the axial end surface of the cylinder sleeve.

[0048] Further, the fluid machine is an expander.

[0049] According to another aspect of the present application, a heat exchange device is provided, comprising a fluid machine, and the fluid machine is the above-mentioned fluid machine.

[0050] According to another aspect of the present application, a method for operating a fluid machine is provided, including self-rotation of a first section of a crankshaft around an axis O0 of the first section, self-rotation of a second section of the crankshaft around an axis O0' of the second section, wherein O0 is not coincident with O0'; the axis O0 of the first section is eccentrically arranged with an axis O1 of a cross-groove structure with a fixed eccentric distance, and the axis O0' of the second section is eccentrically arranged with the axis O1 of the cross-groove structure with a fixed eccentric distance; a first slider makes a circular motion with the axis O0 of the first section as a center, and a distance between a center O3 of the first slider and the axis O0 of the first section is equal to an eccentric amount of an eccentric portion on the first section, and the eccentric amount on the first section is equal to an eccentric distance between the axis O0 of the crankshaft and the axis O1 of the cross-groove structure; the crankshaft rotates to drive the first slider to make a circular motion, and the first slider interacts with the cross-groove structure and reciprocally slides in a limiting channel of the cross-groove structure; a second slider makes a circular motion with the axis O0' of the second section as a center, and a distance between a center O4 of the second slider and the axis O0' of the second section is equal to an eccentric amount of an eccentric portion on the second section, and the eccentric amount on the second section is equal to an eccentric distance between the axis O0' of the second section and the axis O1 of the cross-groove structure; the crankshaft rotates to drive the second slider to make a circular motion, and the second slider interacts with the cross-groove structure and reciprocally slides in a limiting channel of the cross-groove structure.

[0051] Further, the method for operating adopts a principle of a cross slider mechanism, wherein the eccentric portion on the first section is a first connecting rod L1, the eccentric portion on the second section is a second connecting rod L2, and the two limiting channels of the cross-groove structure are respectively a third connecting rod L3 and a fourth connecting rod L4, wherein lengths of the first connecting rod L1 and the second connecting rod L2 are not equal.

[0052] Further, the first connecting rod L1 and the second connecting rod L2 have a first included angle A therebetween, and the third connecting rod L3 and the fourth connecting rod L4 have a second included angle B therebetween, wherein the first included angle A is twice the second included angle B.

[0053] Further, the axis O0 of the first section, the axis O0' of the second section, and the axis O1 of the cross-groove structure have a line O0 O0' O1 therebetween, the first connecting rod L1 has a third included angle C with the line O0 O0' O1, the corresponding third connecting rod L3 has a fourth included angle D with the line O0 O0' 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 line O0 O0' O1, and the corresponding fourth connecting rod L4 has a sixth included angle F with the line O0 O0' O1, wherein the fifth included angle E is twice the sixth included angle F; a sum of the third included angle C and the fifth included angle E is the first included angle A, and a sum of the fourth included angle D and the sixth included angle F is the second included angle B.

[0054] Further, the running method further comprises that the rotation angular velocity of the slider is same as the revolution angular velocity of the slider, and the revolution angular velocity of the cross-groove structure is same as the rotation angular velocity of the slider.

[0055] Further, in the process of the rotation of the crankshaft, the crankshaft rotates 2 rounds, and 4 times of the air intake and exhaust processes are completed.

[0056] According to the technical scheme of the present application, by setting the cross-groove structure as a structure with two limiting channels, and correspondingly setting two sliders, the two eccentric parts of the crankshaft correspondingly extend into the two through holes of the two sliders, and the two sliders correspondingly slide in the two limiting channels and form the 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 at the dead point position, the driving torque of the eccentric part corresponding to the slider at the dead point position is 0, and the slider at the dead point position cannot continue to rotate, while the driving torque of the other eccentric part of the two eccentric parts driving the corresponding slider is the maximum value, which ensures that the eccentric part with the maximum driving torque can normally drive the corresponding slider to rotate, so as to drive the cross-groove structure to rotate through the slider, and then drive the slider at the dead point position to continue to rotate through the cross-groove structure, realizing the stable operation of the fluid machine, avoiding the dead point position of the motion mechanism, and improving the motion reliability of the fluid machine.

[0057] In addition, since the fluid machine provided by the present application can operate stably, that is, the energy efficiency of the compressor is higher, and the noise is smaller, the working reliability of the heat exchange equipment is ensured. BRIEF DESCRIPTION OF DRAWINGS

[0058] The drawings accompanying the specification of the present application form a part thereof, serve to provide further understanding of the present application, and together with the specification explain the present application, and do not constitute an improper limitation to the present application. In the drawings:

[0059] Figure 1 A schematic diagram of the mechanism principle of the compressor running according to an optional embodiment of the present application is shown;

[0060] Figure 2 A schematic diagram of the mechanism principle of the compressor running in Figure 1 is shown;

[0061] Figure 3 A schematic diagram of the internal structure of the compressor according to the first embodiment of the present application is shown;

[0062] Figure 4 A schematic diagram of the structure of the pump body assembly of the compressor in Figure 3 is shown;

[0063] Figure 5 A schematic diagram of theFigure 4 The exploded view of the pump body assembly in

[0064] Figure 6 The assembly view of the crankshaft, cross groove structure, and slider in Figure 5

[0065] Figure 7 The cross-sectional view of the crankshaft, cross groove structure, and slider in Figure 6

[0066] Figure 8 The structure view of the first section of the crankshaft in Figure 5

[0067] Figure 9 The structure view of the first section and the eccentric amount of the eccentric part located on the first section in Figure 8

[0068] Figure 10 The structure view of the second section of the crankshaft in Figure 5

[0069] Figure 11 The structure view of the second section and the eccentric amount of the eccentric part located on the second section in Figure 10

[0070] Figure 12 The structure view of the eccentric amount between the crankshaft and the cylinder sleeve in Figure 4

[0071] Figure 13 The structure view of the cylinder sleeve and the lower flange in the exploded state in Figure 5

[0072] Figure 14 The structure view of the eccentric amount between the cylinder sleeve and the lower flange in Figure 13

[0073] Figure 15 The structure view of the slider in the axial direction of the through hole in Figure 5

[0074] Figure 16 The structure view of the cylinder sleeve in Figure 13

[0075] Figure 17 The structure view of the cylinder sleeve from another perspective in Figure 16

[0076] Figure 18 The cross-sectional view of the cylinder sleeve in Figure 16 ​​​​​​​​​​​​​

[0077] Figure 19 a cross-sectional structural schematic view showing another perspective of the cylinder liner in Figure 16 ;

[0078] Figure 20 a cross-sectional structural schematic view showing another perspective of the cylinder liner in Figure 19 ;

[0079] Figure 21 a cross-sectional structural schematic view showing another perspective of the cylinder liner in Figure 4 , in which the upper flange and the cylinder liner are shown, and in which the exhaust path of the pump body assembly is shown;

[0080] Figure 22 a cross-sectional structural schematic view showing another perspective of the cylinder liner in Figure 5 , in which the cylinder liner and the exhaust cover plate are shown in an exploded state;

[0081] Figure 23 a cross-sectional structural schematic view showing another perspective of the cylinder liner in Figure 3 , in which the compressor is shown at the beginning of the suction;

[0082] Figure 24 a cross-sectional structural schematic view showing another perspective of the cylinder liner in Figure 3 , in which the compressor is shown during the suction;

[0083] Figure 25 a cross-sectional structural schematic view showing another perspective of the cylinder liner in Figure 3 , in which the compressor is shown at the end of the suction;

[0084] Figure 26 a cross-sectional structural schematic view showing another perspective of the cylinder liner in Figure 3 , in which the compressor is shown during the compression of the gas;

[0085] Figure 27 a cross-sectional structural schematic view showing another perspective of the cylinder liner in Figure 3 , in which the compressor is shown during the exhaust;

[0086] Figure 28 a cross-sectional structural schematic view showing another perspective of the cylinder liner in Figure 3 , in which the compressor is shown at the end of the exhaust;

[0087] Figure 29 an exploded structural schematic view of the pump body assembly of the compressor according to the second embodiment of the present application;

[0088] Figure 30 an assembled structural schematic view of the crankshaft, the cross groove structure, and the slider in Figure 29 ;

[0089] Figure 31 an internal structural schematic view of the compressor according to the third embodiment of the present application;

[0090] Figure 32A structural schematic diagram of the pump body assembly of the compressor in Figure 31 A structural schematic diagram of the crankshaft, cross-groove structure, and slider assembly in

[0091] Figure 33 A structural schematic diagram of the crankshaft, cross-groove structure, and slider assembly in Figure 32 A sectional structural schematic diagram of the crankshaft, cross-groove structure, and slider in

[0092] Figure 34 A sectional structural schematic diagram of the crankshaft, cross-groove structure, and slider in Figure 33 A structural schematic diagram of the crankshaft in

[0093] Figure 35 A structural schematic diagram of the crankshaft in Figure 33 A structural schematic diagram of the crankshaft in

[0094] Figure 36 A structural schematic diagram of the crankshaft in Figure 35 A structural schematic diagram of the crankshaft in

[0095] Figure 37 A structural schematic diagram of the first segment and the eccentric amount of the eccentric part located on the first segment in Figure 36 A structural schematic diagram of the second segment and the eccentric amount of the eccentric part located on the second segment in

[0096] Figure 38 A structural schematic diagram of the mechanism principle of the operation of the compressor in the prior art Figure 36 A structural schematic diagram of the mechanism principle of the operation of the compressor in the prior art

[0097] Figure 39 A structural schematic diagram of the mechanism principle of the operation of the compressor in the prior art A structural schematic diagram of the mechanism principle of the operation of the compressor in the prior art

[0098] A structural schematic diagram of the mechanism principle of the operation of the compressor in Figure 40 A structural schematic diagram of the mechanism principle of the operation of the compressor in A structural schematic diagram of the mechanism principle of the operation of the compressor in

[0099] A structural schematic diagram of the mechanism principle of the operation of the compressor in Figure 41 A structural schematic diagram of the mechanism principle of the operation of the compressor in Figure 40 A structural schematic diagram of the mechanism principle of the operation of the compressor in A structural schematic diagram of the mechanism principle of the operation of the compressor in

[0100] A structural schematic diagram of the mechanism principle of the operation of the compressor in Figure 42 A structural schematic diagram of the mechanism principle of the operation of the compressor in Figure 40 A structural schematic diagram of the mechanism principle of the operation of the compressor in A structural schematic diagram of the mechanism principle of the operation of the compressor in

[0101] Wherein, the above drawings include the following reference signs:

[0102] 10, crankshaft; 11, eccentric part; 12, shaft body part; 121, first segment; 1211, first protruding structure; 122, second segment; 1221, second protruding structure; 13, sliding connecting piece; 131, limiting sliding groove

[0103] 20, cylinder liner; 21, compression inlet; 22, compression outlet; 23, suction chamber; 24, suction communication chamber; 25, exhaust chamber; 26, communication hole;

[0104] 30, cross groove structure; 31, limiting channel; 311, variable volume chamber; 32, center hole;

[0105] 40, slider; 41, through hole; 42, extrusion surface;

[0106] 50, flange; 51, exhaust passage; 52, upper flange; 53, lower flange;

[0107] 60, exhaust valve assembly; 61, exhaust valve plate; 62, valve plate baffle;

[0108] 70, exhaust cover plate;

[0109] 80, distributor component; 81, housing assembly; 82, motor assembly; 83, pump body assembly; 84, upper cover assembly; 85, lower cover assembly;

[0110] 90, fastener. DETAILED DESCRIPTION

[0111] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. The description of the at least one exemplary embodiment is actually only illustrative, but not as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0112] In the prior art, as shown in Figure 39 , a compressor operating mechanism principle is proposed based on a cross slider mechanism, that is, taking point O1 as the center of the cylinder, point O2 as the center of the driving shaft, and point O3 as the center of the slider, the cylinder and the driving shaft are eccentrically arranged, wherein the slider center O3 makes a circular motion on a circle with a diameter of O1O2.

[0113] In the above operating mechanism principle, the cylinder center O1 and the driving shaft center O2 are the two rotation centers of the motion mechanism, and at the same time, the midpoint O0 of the line segment O1O2 is the virtual center of the slider center O3, so that the slider makes a reciprocating motion relative to the cylinder, and the slider also makes a reciprocating motion relative to the driving shaft.

[0114] Since the midpoint O0 of the line segment O1O2 is a virtual center, it is impossible to set a balance system, which leads to the problem of deterioration of the high-frequency vibration characteristics of the compressor. On the basis of the above operating mechanism principle, as shown in Figure 40As shown, a motion mechanism with O0 as the driving shaft center is proposed, that is, the cylinder center O1 and the driving shaft center O0 are two rotation centers of the motion mechanism, the driving shaft has an eccentric part, the slider is coaxially arranged with the eccentric part, and the assembly eccentricity of the driving shaft and the cylinder is equal to the eccentricity of the eccentric part, so that the slider center O3 makes a circular motion with the driving shaft center O0 as the center and O1O0 as the radius.

[0115] Correspondingly, a set of operation mechanism is proposed, which comprises a cylinder, a limiting groove structure, a slider and a driving shaft, wherein the limiting groove structure is rotatably arranged in the cylinder, and the cylinder and the limiting groove structure are coaxially arranged, that is, the cylinder center O1 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 driving shaft, and the slider makes a circular motion around the shaft body part of the driving shaft, and specifically, the motion process is as follows: the driving shaft rotates to drive the slider to revolve around the center of the shaft body part of the driving shaft, the slider simultaneously rotates relative to the eccentric part, and the slider reciprocates in the limiting groove of the limiting groove structure and drives the limiting groove structure to rotate.

[0116] However, as Figure 41 shown, the length of the force arm L of the driving shaft driving the slider to rotate is L=2e*cos theta*cos theta, wherein e is the eccentricity of the eccentric part, and theta is the included angle between the O1O0 connecting line and the sliding direction of the slider in the limiting groove.

[0117] As Figure 42 shown, when the cylinder center O1 (that is, the center of the limiting groove structure) and the center of the eccentric part coincide, the resultant force of the driving force of the driving shaft passes through the center of the limiting groove structure, that is, the torque applied on the limiting groove structure is zero, and the limiting groove structure cannot rotate, at this time, the motion mechanism is in a dead point position and cannot drive the slider to rotate.

[0118] Based on this, the application proposes a brand new mechanism principle with a cross groove structure with two limiting channels and double sliders, and a brand new compressor is constructed based on the principle, and the compressor has the characteristics of high energy efficiency and low noise, and the compressor is taken as an example to specifically introduce the compressor based on the cross groove structure with two limiting channels and double sliders.

[0119] In order to solve the problems of low energy efficiency and large noise of the compressor in the prior art, the application provides a fluid machine, a heat exchange device and a running method of the fluid machine, wherein the heat exchange device comprises the fluid machine described below, and the fluid machine runs by using the running method described below.

[0120] The fluid machine comprises a crankshaft 10, a cylinder sleeve 20, a cross groove structure 30 and a sliding block 40, wherein the crankshaft 10 is provided with two eccentric parts 11 along the axial direction of the crankshaft 10, the two eccentric parts 11 have a phase difference of a first included angle A, and the eccentricity of the two eccentric parts 11 is not equal; the crankshaft 10 is eccentrically arranged with the cylinder sleeve 20 and the eccentric distance is fixed; the cross groove structure 30 is rotatably arranged in the cylinder sleeve 20, the cross groove structure 30 has two limiting channels 31, the two limiting channels 31 are sequentially arranged along the axial direction of the crankshaft 10, the extension direction of the limiting channel 31 is perpendicular to the axial direction of the crankshaft 10, and the extension directions of the two limiting channels 31 have a phase difference of a second included angle B, wherein the first included angle A is twice the second included angle B; the sliding block 40 has a through hole 41, and the sliding block 40 is two, the two eccentric parts 11 correspondingly extend into the two through holes 41 of the two sliding blocks 40, and the two sliding blocks 40 are correspondingly arranged in the two limiting channels 31 and form a variable volume cavity 311, the variable volume cavity 311 is located in the sliding direction of the sliding block 40, and when the crankshaft 10 rotates to drive the sliding block 40 to reciprocally slide in the limiting channel 31, the cross groove structure 30 and the sliding block 40 rotate in the cylinder sleeve 20.

[0121] By arranging the cross groove structure 30 in the form of two limiting channels 31 and correspondingly arranging two sliding blocks 40, the two eccentric parts 11 of the crankshaft correspondingly extend into the two through holes 41 of the two sliding blocks 40, and at the same time, the two sliding blocks 40 are correspondingly arranged in the two limiting channels 31 and form a variable volume cavity 311, since the first included angle A between the two eccentric parts 11 is twice the second included angle B between the extension directions of the two limiting channels 31, when one of the two sliding blocks 40 is at a dead center position, the driving torque of the eccentric part 11 corresponding to the sliding block 40 at the dead center position is 0, and the sliding block 40 at the dead center position cannot continue to rotate, while the driving torque of the other eccentric part 11 of the two eccentric parts 11 driving the corresponding sliding block 40 is the maximum value, which ensures that the eccentric part 11 with the maximum driving torque can normally drive the corresponding sliding block 40 to rotate, thereby driving the cross groove structure 30 to rotate through the sliding block 40, and further driving the sliding block 40 at the dead center position to continue to rotate through the cross groove structure 30, realizing stable operation of the fluid machine, avoiding the dead center position of the movement mechanism, and improving the movement reliability of the fluid machine, thereby ensuring the working reliability of the heat exchange equipment.

[0122] In addition, the fluid machine provided by the present application can stably operate, that is, the energy efficiency of the compressor is higher, the noise is smaller, thereby ensuring the working reliability of the heat exchange equipment.

[0123] It should be noted that in the present application, the first included angle A and the second included angle B are not zero.

[0124] As Figure 1and Figure 2 As shown in the above fluid machine operation, the operation method of the fluid machine includes the first section 121 of the crankshaft 10 rotating around the axis O0 of the first section 121, the second section 122 of the crankshaft 10 rotating around the axis O0' of the second section 122, wherein O0 and O0' are not coincident; the axis O0 of the first section 121 is eccentrically arranged with the axis O1 of the cross-groove structure 30 and the eccentric distance is fixed, the axis O0' of the second section 122 is eccentrically arranged with the axis O1 of the cross-groove structure 30 and the eccentric distance is fixed; the first slider 40 makes a circular motion with the axis O0 of the first section 121 as the center, and the distance between the center O3 of the first slider 40 and the axis O0 of the first section 121 is equal to the eccentric amount of the eccentric part 11 on the first section 121, and the eccentric amount of the first section 121 is equal to the eccentric distance between the axis O0 of the crankshaft 10 and the axis O1 of the cross-groove structure 30; the crankshaft 10 rotates to drive the first slider 40 to make a circular motion, and the first slider 40 interacts with the cross-groove structure 30 and reciprocally slides in the limiting channel 31 of the cross-groove structure 30; the second slider 40 makes a circular motion with the axis O0' of the second section 122 as the center, and the distance between the center O4 of the second slider 40 and the axis O0' of the second section 122 is equal to the eccentric amount of the eccentric part 11 on the second section 122, and the eccentric amount of the second section 122 is equal to the eccentric distance between the axis O0' of the second section 122 and the axis O1 of the cross-groove structure 30; the crankshaft 10 rotates to drive the second slider 40 to make a circular motion, and the second slider 40 interacts with the cross-groove structure 30 and reciprocally slides in the limiting channel 31 of the cross-groove structure 30.

[0125] The fluid machine as described above operates as a cross slider mechanism, and the operation method adopts the principle of the cross slider 40 mechanism, wherein the eccentric part 11 on the first section 121 is the first connecting rod L1, the eccentric part 11 on the second section 122 is the second connecting rod L2, and the two limiting channels 31 of the cross-groove structure 30 are the third connecting rod L3 and the fourth connecting rod L4, respectively, wherein the lengths of the first connecting rod L1 and the second connecting rod L2 are not equal.

[0126] As shown in the above cross slider mechanism, the first connecting rod L1 and the second connecting rod L2 have a first included angle A, and the third connecting rod L3 and the fourth connecting rod L4 have a second included angle B, wherein the first included angle A is twice the second included angle B. Figure 1

[0127] As shown in the above cross slider mechanism, the first connecting rod L1 and the second connecting rod L2 have a first included angle A, and the third connecting rod L3 and the fourth connecting rod L4 have a second included angle B, wherein the first included angle A is twice the second included angle B. Figure 2 ​As shown, the line between the axis O0 of the first section 121, the axis O0' of the second section 122 and the axis O1 of the cross groove structure 30 is the line O0 O0' O1, the first connecting rod L1 has a third included angle C with the line O0 O0' O1, the corresponding third connecting rod L3 has a fourth included angle D with the line O0 O0' 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 line O0 O0' O1, the corresponding fourth connecting rod L4 has a sixth included angle F with the line O0 O0' 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.

[0128] Further, the operation method further comprises that the angular velocity of the revolution of the slider 40 is the same as the angular velocity of the revolution of the slider 40; the angular velocity of the revolution of the cross groove structure 30 is the same as the angular velocity of the revolution of the slider 40.

[0129] Specifically, the axis O0 of the first section 121 corresponds to the rotation center of the first connecting rod L1, the axis O0' of the second section 122 corresponds to the rotation center of the second connecting rod L2, and the axis O1 of the cross-slot structure 30 corresponds to the rotation center of the third connecting rod L3 and the fourth connecting rod L4; the two eccentric parts 11 of the crankshaft 10 respectively serve as the first connecting rod L1 and the second connecting rod L2, the two limiting channels 31 of the cross-slot structure 30 respectively serve as the third connecting rod L3 and the fourth connecting rod L4, and the lengths of the first connecting rod L1 and the second connecting rod L2 are not equal, so that the first section 121 rotates, the eccentric part 11 on the first section 121 drives the corresponding slider 40 to revolve around the axis O0 of the first section 121, and the slider 40 can rotate relative to the eccentric part 11, and the relative rotation speeds of the two are the same, since the first slider 40 and the second slider 40 reciprocate in the two corresponding limiting channels 31 and drive the cross-slot structure 30 to move in a circle, limited by the two limiting channels 31 of the cross-slot structure 30, the movement directions of the two sliders 40 always have a phase difference of the second included angle B, when the eccentric part 11 on the first section 121 is at the dead point position, the eccentric part 11 on the second section 122 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-slot structure 30 to rotate through the slider 40, and further driving the slider 40 at the dead point position to continue rotating through the cross-slot structure 30, realizing stable operation of the fluid machine, avoiding the dead point position of the movement mechanism, improving the movement reliability of the fluid machine, and thus ensuring the working reliability of the heat exchange equipment; or, when the eccentric part 11 on the second section 122 is at the dead point position, the eccentric part 11 on the first section 121 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-slot structure 30 to rotate through the slider 40, and further driving the slider 40 at the dead point position to continue rotating through the cross-slot structure 30, realizing stable operation of the fluid machine, avoiding the dead point position of the movement mechanism, improving the movement reliability of the fluid machine, and thus ensuring the working reliability of the heat exchange equipment.

[0130] It should be noted that, in the present application, the maximum force arm of the driving torque of the eccentric part 11 is 2e.

[0131] In this movement method, the running tracks of the sliders 40 are both circles, one of which has the axis O0 of the first section 121 as the center and the line O0 O1 as the radius, and the other of which has the axis O0' of the second section 122 as the center and the line O0' O1 as the radius.

[0132] It should be noted that, in the present application, in the process of rotation of the crankshaft 10, the crankshaft 10 rotates 2 circles, and completes 4 times of suction and exhaust processes.

[0133] Three optional embodiments will be given below to introduce the structure of the fluid machine in detail, so as to better illustrate the operation method of the fluid machine through the structural features.

[0134] Embodiment one

[0135] As shown in Figures 3 to 28 , the shaft body part 12 of the crankshaft 10 comprises a first section 121 and a second section 122 connected along the axial direction thereof, the first section 121 and the second section 122 are arranged in different axial directions and are movably connected, and the two eccentric parts 11 are arranged on the first section 121 and the second section 122 respectively. In this way, by arranging the shaft body part 12 of the crankshaft 10 as the first section 121 and the second section 122 connected along the axial direction thereof, while the first section 121 and the second section 122 are arranged in different axial directions and are movably connected, it is ensured that the eccentric amounts of the eccentric parts 11 on the first section 121 and the second section 122 are not equal, and at the same time, the rotation reliability of the first section 121 and the second section 122 is ensured.

[0136] As shown in Figure 5 , the crankshaft 10 further comprises a sliding connecting piece 13, the first section 121 is movably connected with the second section 122 through the sliding connecting piece 13, the first section 121 rotates while the sliding connecting piece 13 slides relative to the first section 121, and the second section 122 rotates while the sliding connecting piece 13 slides relative to the second section 122. In this way, by using the sliding connecting piece 13, the rotation reliability between the first section 121 and the second section 122 is ensured while the first section 121 and the second section 122 are arranged in different axial directions.

[0137] As shown in Figure 5As shown, the sliding connector 13 has two limiting sliding grooves 131, the extending directions of the two limiting sliding grooves 131 are perpendicular to the axial direction of the crankshaft 10, and the extending directions of the two limiting sliding grooves 131 are perpendicular to each other; the end of the first section 121 towards one side of the sliding connector 13 has a first protruding structure 1211, the end of the second section 122 towards one side of the sliding connector 13 has a second protruding structure 1221, and the first protruding structure 1211 and the second protruding structure 1221 are respectively slidably arranged in the two limiting sliding grooves 131; the first section 121 rotates to make the first protruding structure 1211 reciprocally slide in the corresponding limiting sliding groove 131 while interacting with the sliding connector 13, the sliding connector 13 rotates and drives the second protruding structure 1221 to reciprocally slide in the corresponding limiting sliding groove 131 while driving the second section 122 to rotate; or, the second section 122 rotates to make the second protruding structure 1221 reciprocally slide in the corresponding limiting sliding groove 131 while interacting with the sliding connector 13, the sliding connector 13 rotates and drives the first protruding structure 1211 to reciprocally slide in the corresponding limiting sliding groove 131 while driving the first section 121 to rotate. In this way, the connection reliability of the first section 121 and the second section 122 is ensured, and the rotation stability between the two is also ensured.

[0138] As shown in Figure 9 , Figure 11 , Figure 12 and Figure 14 , the assembly eccentric amount of the first section 121 and the cylinder sleeve 20 is equal to the eccentric amount of the eccentric part 11 arranged on the first section 121, and the assembly eccentric amount of the second section 122 and the cylinder sleeve 20 is equal to the eccentric amount of the eccentric part 11 arranged on the second section 122. In this way, Figure 9 , the eccentric amount of the eccentric part 11 on the first section 121 is e1, Figure 14 , the assembly eccentric amount of the first section 121 and the cylinder sleeve 20 is also e1, and Figure 11 , the eccentric amount of the eccentric part 11 on the second section 122 is e2, Figure 14 , the assembly eccentric amount of the second section 122 and the cylinder sleeve 20 is also e2, and Figure 1 and Figure 2 , the motion reliability of the motion mechanism constructed is ensured.

[0139] As shown in Figure 12 , the label H1 represents the axis of the first section 121, the label H1 represents the axis of the second section 122, and the label I represents the axis of the inner ring of the cylinder sleeve 20.

[0140] As shown in Figure 5 , the two ends of the limiting channel 31 pass through to the outer circumferential surface of the cross groove structure 30. In this way, it is beneficial to reduce the machining and manufacturing difficulty of the cross groove structure 30.

[0141] Optionally, the two sliding blocks 40 are arranged concentrically with the two eccentric parts 11, and the sliding blocks 40 move in a circular motion around the shaft center of the crankshaft 10, and the hole wall of the through hole 41 and the eccentric part 11 have a first rotation gap, and the range of the first rotation gap is 0.005mm-0.05mm.

[0142] Optionally, the cross groove structure 30 is arranged coaxially with the cylinder sleeve 20, and the outer circumferential surface of the cross groove structure 30 and the inner wall surface of the cylinder sleeve 20 have a second rotation gap, and the size of the second rotation gap is 0.005mm-0.1mm.

[0143] It should be noted that in the present application, the first included angle A is 160-200 degrees, and the second included angle B is 80-100 degrees. In this way, as long as the first included angle A is twice the second included angle B, the relationship can be met.

[0144] Preferably, the first included angle A is 160 degrees, and the second included angle B is 80 degrees.

[0145] Preferably, the first included angle A is 165 degrees, and the second included angle B is 82.5 degrees.

[0146] Preferably, the first included angle A is 170 degrees, and the second included angle B is 85 degrees.

[0147] Preferably, the first included angle A is 175 degrees, and the second included angle B is 87.5 degrees.

[0148] Preferably, the first included angle A is 180 degrees, and the second included angle B is 90 degrees.

[0149] Preferably, the first included angle A is 185 degrees, and the second included angle B is 92.5 degrees.

[0150] Preferably, the first included angle A is 190 degrees, and the second included angle B is 95 degrees.

[0151] Preferably, the first included angle A is 195 degrees, and the second included angle B is 97.5 degrees.

[0152] As Figure 4 , Figure 5 and Figure 12As 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.

[0153] 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.

[0154] Preferably, the range of the first assembly gap is 0.01 to 0.03 mm.

[0155] 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.

[0156] like Figures 4 to 12 As shown, the eccentric part 11 is cylindrical.

[0157] Optionally, the proximal end of the eccentric portion 11 is flush with the outer circle of the shaft portion 12 of the crankshaft 10.

[0158] Optionally, the proximal end of the eccentric portion 11 protrudes beyond the outer circle of the shaft portion 12 of the crankshaft 10.

[0159] Optionally, the proximal end of the eccentric portion 11 is located inside the outer circle of the shaft portion 12 of the crankshaft 10.

[0160] 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.

[0161] like Figures 4 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.

[0162] like Figure 5As shown, the cross-groove structure 30 has a central hole 32, through which two limiting channels 31 are connected. The diameter of the central 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 central hole 32.

[0163] 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.

[0164] like Figure 15 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.

[0165] 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. Figure 15 In the middle, the center of the through hole 41 of the slider 40 is O. 滑块 The distance between the center of the two arc surfaces and the center of the through hole 41 is 'e', ​​that is, the eccentricity of the eccentric part 11. Figure 15 The dashed X-line in the diagram represents the circle containing the center of the two arc surfaces.

[0166] Optionally, 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, the difference being in the range of -0.05mm to 0.025mm.

[0167] Preferably, the difference ranges from -0.02 to 0.02 mm.

[0168] 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.

[0169] Preferably, S 滑块 / S 排 The value is 12 to 18.

[0170] 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.

[0171] Alternatively, the above-mentioned components can be connected by welding, heat fitting, or cold pressing.

[0172] The assembly process of the entire pump body assembly 83 is as follows: The lower flange 53 is fixed on the cylinder liner 20, and the two sliders 40 are respectively placed in the corresponding two limiting channels 31. After assembling the first section 121, the second section 122, and the sliding connector 13 into the crankshaft 10, 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, the cross groove structure 30, and the two sliders 40 are placed in the cylinder liner 20. One end of the crankshaft 10 is installed 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 .

[0173] 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.

[0174] 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 28During 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.

[0175] 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 25 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.

[0176] Specifically, such as Figure 13 , Figures 16 to 28 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.

[0177] like Figure 13 , Figures 16 to 28 As 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.

[0178] 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.

[0179] Specifically, the suction cavity 23 extends around the inner wall surface of the cylinder sleeve 20 by a first preset distance to form an arc-shaped suction cavity 23. In this way, the volume of the suction cavity 23 is ensured to be large enough to store a large amount of gas.

[0180] As shown in Figure 13 , Figure 16 and Figure 18 , the suction cavity 23 is two, the two suction cavities 23 are arranged axially spaced apart from each other on the cylinder sleeve 20, the cylinder sleeve 20 further has a suction communication cavity 24, the two suction cavities 23 are in communication with the suction communication cavity 24, and the compression intake port 21 is in communication with the suction cavities 23 through the suction communication cavity 24. In this way, it is beneficial to increase the volume of the suction cavity 23, thereby reducing the suction pressure pulsation.

[0181] Optionally, the suction communication cavity 24 extends along the axial direction of the cylinder sleeve 20 by a second preset distance, and at least one end of the suction communication cavity 24 penetrates through the axial end surface of the cylinder sleeve 20. In this way, it is convenient to open the suction communication cavity 24 from the end surface of the cylinder sleeve 20, and the machining convenience of the suction communication cavity 24 is ensured.

[0182] As shown in Figure 13 , Figure 16 and Figure 18 , the outer wall of the cylinder sleeve 20 is provided with an exhaust cavity 25, the compression exhaust port 22 is communicated to the exhaust cavity 25 from the inner wall of the cylinder sleeve 20, and the fluid machine further comprises an exhaust valve assembly 60, which is arranged in the exhaust cavity 25 and corresponds to the compression exhaust port 22. In this way, the exhaust cavity 25 is used to accommodate the exhaust valve assembly 60, effectively reducing the occupied space of the exhaust valve assembly 60, reasonably arranging the components, and improving the space utilization rate of the cylinder sleeve 20.

[0183] As shown in Figures 18 to 21 , the compression exhaust port 22 is two, the two compression exhaust ports 22 are arranged axially spaced apart from each other on the cylinder sleeve 20, and the exhaust valve assembly 60 is two groups, and the two groups of exhaust valve assemblies 60 are arranged corresponding to the two compression exhaust ports 22 respectively. In this way, since the two compression exhaust ports 22 are respectively provided with two groups of exhaust valve assemblies 60, the gas in the variable volume cavity 311 is effectively prevented from leaking in large quantities, and the compression efficiency of the variable volume cavity 311 is ensured.

[0184] As shown in Figure 19 , the exhaust valve assembly 60 is connected with the cylinder sleeve 20 through a fastener 90, the exhaust valve assembly 60 comprises an exhaust valve plate 61 and a valve plate baffle 62, the exhaust valve plate 61 is arranged in the exhaust cavity 25 and shields the corresponding compression exhaust port 22, and the valve plate baffle 62 is arranged overlappingly on the exhaust valve plate 61. In this way, the arrangement of the valve plate baffle 62 effectively avoids the excessive opening of the exhaust valve plate 61, thereby ensuring the exhaust performance of the cylinder sleeve 20.

[0185] Optionally, the fastener 90 is a screw.

[0186] As shown in Figure 13 , Figure 16 and Figure 21 , the axial end surface of the cylinder sleeve 20 is further provided with a communication hole 26, the communication hole 26 is in communication with the exhaust cavity 25, and the fluid machine further comprises a flange 50, the flange 50 is provided with an exhaust passage 51, and the communication hole 26 is in communication with the exhaust passage 51. In this way, the exhaust reliability of the cylinder sleeve 20 is ensured.

[0187] As shown in Figure 22 , the exhaust cavity 25 penetrates to the outer wall surface of the cylinder sleeve 20, and the fluid machine further comprises an exhaust cover plate 70, which is connected with the cylinder sleeve 20 and seals the exhaust cavity 25. In this way, the exhaust cover plate 70 plays a role of separating the variable volume cavity 311 from the external space of the pump body assembly 83.

[0188] It should be noted that in the present application, when the variable volume cavity 311 is in communication with the compression exhaust port 22, the pressure of the variable volume cavity 311 reaches the exhaust pressure, the exhaust valve plate 61 is opened, the compressed gas enters the exhaust cavity 25 through the compression exhaust port 22, and then passes through the communication hole 26 on the cylinder sleeve 20, and then is discharged through the exhaust passage 51 and enters the external space of the pump body assembly 83 (i.e. the cavity of the compressor), thereby completing the exhaust process.

[0189] Optionally, the exhaust cover plate 70 is fixed on the cylinder sleeve 20 by a fastener 90.

[0190] Optionally, the fastener 90 is a screw.

[0191] Optionally, the outer contour of the exhaust cover plate 70 is matched with the outer contour of the exhaust cavity 25.

[0192] The operation of the compressor will be described in detail as follows:

[0193] As shown in Figure 3 , the motor assembly 82 drives the rotation of the crankshaft 10, and the two eccentric parts 11 of the crankshaft 10 drive the corresponding two sliders 40 to move, respectively. The slider 40 revolves around the axis of the crankshaft 10 while the slider 40 rotates relative to the eccentric part 11, and the slider 40 reciprocates along the limiting channel 31 and drives the cross groove structure 30 to rotate in the cylinder sleeve 20. The slider 40 revolves while reciprocating along the limiting channel 31 to form a cross slider mechanism movement mode.

[0194] Other use occasions: the compressor exchanges the positions of the suction and exhaust ports, which can be used as an expander. That is, the exhaust port of the compressor is used as the suction port of the expander, high-pressure gas is introduced, other driving mechanisms rotate, and the gas is discharged after expansion through the compressor suction port (expander exhaust port).

[0195] When the fluid machine is an expander, the cylinder sleeve 20 has an expansion exhaust port and an expansion intake port, the expansion exhaust port is communicated with the corresponding variable volume chamber 311 when any one of the sliders 40 is in the intake position; the corresponding variable volume chamber 311 is communicated with the expansion intake port when any one of the sliders 40 is in the exhaust position.

[0196] Optionally, the inner wall surface of the cylinder sleeve 20 has an expansion exhaust chamber 25, the expansion exhaust chamber 25 is communicated with the expansion exhaust port.

[0197] Further, the expansion exhaust chamber 25 extends along the circumference of the inner wall surface of the cylinder sleeve 20 by a first preset distance to form an arc-shaped expansion exhaust chamber 25, and the expansion exhaust chamber 25 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 25 is the same as the rotation direction of the cross groove structure 30.

[0198] Further, the expansion exhaust chamber 25 is two, the two expansion exhaust chambers 25 are arranged in the axial direction of the cylinder sleeve 20, and the cylinder sleeve 20 further has an expansion exhaust communication chamber, the two expansion exhaust chambers 25 are both communicated with the expansion exhaust communication chamber, and the expansion exhaust port is communicated with the expansion exhaust chamber 25 through the expansion exhaust communication chamber.

[0199] Further, the expansion exhaust communication chamber extends along the axial direction of the cylinder sleeve 20 by a second preset distance, and at least one end of the expansion exhaust communication chamber penetrates the axial end surface of the cylinder sleeve 20.

[0200] Embodiment Two

[0201] As shown in Figure 29 and Figures 31 to 38 The difference between the present embodiment and embodiment one is that the cross section of the limiting channel 31 of the cross groove structure 30 is square, and the cross section of the corresponding slider 40 in the sliding direction is square which is adapted to the limiting channel.

[0202] It should be noted that the suction and exhaust mode of embodiment one is also applicable to the present embodiment, which will not be described here.

[0203] Embodiment Three

[0204] As shown in ​As shown, the difference between the embodiment and embodiment one is that the sliding connecting piece 13 has two limiting protrusions respectively extending towards the first section 121 and the second section 122; the end of the first section 121 towards one side of the sliding connecting piece 13 has a first sliding groove structure, the end of the second section 122 towards one side of the sliding connecting piece 13 has a second sliding groove structure, the two limiting protrusions are respectively slidingly arranged in the first sliding groove structure and the second sliding groove structure, and the extension direction of the first sliding groove structure is perpendicular to the extension direction of the second sliding groove structure; the first section 121 rotates to make the corresponding limiting protrusion reciprocally slide in the first sliding groove structure, at the same time, the first sliding groove structure interacts with the sliding connecting piece 13, the sliding connecting piece 13 rotates and drives the second section 122 to rotate while driving the limiting protrusion to reciprocally slide in the second sliding groove structure; or, the second section 122 rotates to make the corresponding limiting protrusion reciprocally slide in the second sliding groove structure, at the same time, the second sliding groove structure interacts with the sliding connecting piece 13, the sliding connecting piece 13 rotates and drives the first section 121 to rotate while driving the limiting protrusion to reciprocally slide in the first sliding groove structure. In this way, the connection reliability of the first section 121 and the second section 122 is ensured, and the rotation stability between the two is also ensured.

[0205] It should be noted that the air suction and exhaust mode of embodiment one is also applicable to the present embodiment, which will not be repeated here.

[0206] It should be noted that the terms used herein are only intended to describe specific embodiments and are not intended to limit exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form, unless the context clearly indicates otherwise, and it should also be understood that when the terms "comprise" and / or "include" are used in the specification, they indicate the presence of the features, steps, operations, devices, components and / or combinations thereof.

[0207] Unless otherwise specifically stated, the relative arrangements of parts and steps, numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the application. At the same time, it should be understood that the sizes of the various parts shown in the drawings are not drawn in proportion to the actual proportions. The techniques, methods and devices known to those skilled in the relevant art can not be discussed in detail, but under appropriate circumstances, the techniques, methods and devices should be considered as part of the authorized specification. In all examples shown and discussed herein, any specific value should be interpreted as merely exemplary, and not as a limitation. Therefore, other examples of exemplary embodiments can have different values. It should be noted that similar reference numbers and letters represent similar items in the following drawings, so once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0208] For purposes of the description hereinafter, the terms "upper", "lower", "right", "left", "rear", "front", "vertical", "horizontal", and derivatives thereof shall relate to the application as it is oriented in the drawing figures. The terms "on", "above", "under", "below" and derivatives thereof shall relate to the application as it is oriented in the drawing figures. Where, for purposes of clarity, or the like, directional terms are used in the description herein (e.g., "forward", "rearward", "up", "down", "left", "right", "vertical", "horizontal", "upper", "lower", "above", "below", "upward", "downward", "top", "bottom" and the like), it is understood that these terms are used to facilitate the description of the application, and do not limit the scope of the application. For example, if the application is turned over, or rotated 90 degrees, or inverted, the directional terms are reversed. Accordingly, the directional terms are interchangeable under appropriate circumstances such that the application described herein describes the application in one orientation, and is equally applicable to other orientations, unless otherwise specifically noted.

[0209] It is also important to note that the term "or" as used herein is intended to mean any of the possible options. For example, if X or Y or both are present, that covers the options of X being present and Y being absent, Y being present and X being absent, and both X and Y being present.

[0210] It should be noted that the terms "first", "second", and the like, used herein do not necessarily have an ordinal meaning. Rather these terms are generally used to distinguish or identify different structures. Thus, such terms are also inter-changeable under appropriate circumstances. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the present application. Thus, for example, as used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising", when used in this specification, specify the presence of stated features, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or groups thereof.

[0211] The specific embodiments described herein are illustrative examples of one or more aspects of the present application and, accordingly, it will be apparent to those of ordinary skill in the art that numerous modifications and variations can be made without departing from the spirit and scope of the application. Accordingly, the entire disclosure of each of the above cited references is totally incorporated by reference herein, and in the event of a conflict between the disclosure herein and the above cited references, the disclosure herein will control.

Claims

1. A fluid machine characterized by, The application relates to a fluid machine comprising: a crankshaft (10) provided with two eccentric portions (11) along the axial direction of the crankshaft (10), the two eccentric portions (11) having a first included angle A of the phase difference, and the eccentricity of the two eccentric portions (11) being unequal; a cylinder sleeve (20) eccentrically arranged with the crankshaft (10) and fixed with the eccentric distance; a cross-groove structure (30) rotatably arranged in the cylinder sleeve (20), the cross-groove structure (30) having two limiting channels (31) sequentially arranged along the axial direction of the crankshaft (10), the extending direction of the limiting channels (31) being perpendicular to the axial direction of the crankshaft (10), and the extending direction of the two limiting channels (31) having a second included angle B of the phase difference, wherein the first included angle A is twice the second included angle B; two sliders (40) having through holes (41), the two eccentric portions (11) corresponding to the two sliders (40) extending into the two through holes (41) of the two sliders (40), and the two sliders (40) corresponding to the two limiting channels (31) and forming a variable volume cavity (311) in the sliding direction of the sliders (40), the crankshaft (10) rotating to drive the sliders (40) to reciprocatingly slide in the limiting channels (31) and interact with the cross-groove structure (30), so that the cross-groove structure (30) and the sliders (40) rotate in the cylinder sleeve (20).

2. The fluid machine of claim 1, wherein, The shaft body portion (12) of the crankshaft (10) comprises a first segment (121) and a second segment (122) connected along the axial direction, the first segment (121) and the second segment (122) being arranged in different axes and movably connected, and the two eccentric portions (11) being arranged on the first segment (121) and the second segment (122) respectively.

3. The fluid machine of claim 2, wherein, The crankshaft (10) further comprises a sliding connector (13), the first segment (121) being movably connected with the second segment (122) through the sliding connector (13), the sliding connector (13) sliding relative to the first segment (121) while the first segment (121) rotates, and the sliding connector (13) sliding relative to the second segment (122) while the second segment (122) rotates.

4. The fluid machine according to claim 3, wherein the sliding connector (13) has two limiting sliding grooves (131), the extending direction of the two limiting sliding grooves (131) being perpendicular to the axial direction of the crankshaft (10), and the extending direction of the two limiting sliding grooves (131) being perpendicular to each other. The first segment (121) has a first protruding structure (1211) at the end of the side of the sliding connector (13), and the second segment (122) has a second protruding structure (1221) at the end of the side of the sliding connector (13), and the first protruding structure (1211) and the second protruding structure (1221) are respectively slidably arranged in two limiting sliding grooves (131); The first segment (121) rotates to make the first protruding structure (1211) reciprocally slide in the corresponding limiting sliding groove (131) while interacting with the sliding connector (13), and the sliding connector (13) rotates to drive the second segment (122) to rotate while making the second protruding structure (1221) reciprocally slide in the corresponding limiting sliding groove (131); or, The second segment (122) rotates to make the second protruding structure (1221) reciprocally slide in the corresponding limiting sliding groove (131) while interacting with the sliding connector (13), and the sliding connector (13) rotates to drive the first segment (121) to rotate while making the first protruding structure (1211) reciprocally slide in the corresponding limiting sliding groove (131).

5. The fluid machine according to claim 3, wherein The sliding connector (13) has two limiting protrusions respectively protruding towards the first segment (121) and the second segment (122); The first segment (121) has a first sliding groove structure at the end of the side of the sliding connector (13), and the second segment (122) has a second sliding groove structure at the end of the side of the sliding connector (13), and the two limiting protrusions are respectively slidably arranged in the first sliding groove structure and the second sliding groove structure, and the extension direction of the first sliding groove structure is perpendicular to the extension direction of the second sliding groove structure; The first segment (121) rotates to make the corresponding limiting protrusion reciprocally slide in the first sliding groove structure while the first sliding groove structure interacts with the sliding connector (13), and the sliding connector (13) rotates to drive the second segment (122) to rotate while making the limiting protrusion reciprocally slide in the second sliding groove structure; or, The second segment (122) rotates to make the corresponding limiting protrusion reciprocally slide in the second sliding groove structure while the second sliding groove structure interacts with the sliding connector (13), and the sliding connector (13) rotates to drive the first segment (121) to rotate while making the limiting protrusion reciprocally slide in the first sliding groove structure.

6. The fluid machine of claim 2, wherein, The assembly eccentricity of the first segment (121) and the cylinder sleeve (20) is equal to the eccentricity of the eccentric part (11) arranged on the first segment (121), and the assembly eccentricity of the second segment (122) and the cylinder sleeve (20) is equal to the eccentricity of the eccentric part (11) arranged on the second segment (122).

7. The fluid machine of claim 1, wherein, Two ends of the limiting channel (31) pass through to the outer circumferential surface of the cross groove structure (30).

8. The fluid machine of claim 1, wherein, The two sliding blocks (40) are respectively arranged concentrically with the two eccentric parts (11), the sliding block (40) performs circumferential motion around the shaft center of the crankshaft (10), the hole wall of the through hole (41) and the eccentric part (11) have a first rotation gap, and the first rotation gap ranges from 0.005 mm to 0.05 mm.

9. The fluid machine of claim 1, wherein, The cross groove structure (30) is arranged coaxially with the cylinder sleeve (20), and the outer circumferential surface of the cross groove structure (30) and the inner wall surface of the cylinder sleeve (20) have a second rotation gap, and the size of the second rotation gap ranges from 0.005 mm to 0.1 mm.

10. The fluid machine of claim 1, wherein, The first included angle A is 160 degrees to 200 degrees; and the second included angle B is 80 degrees to 100 degrees.

11. The fluid machine of claim 1, wherein, The fluid machine further comprises a flange (50), the flange (50) is arranged at the axial end of the cylinder sleeve (20), and the crankshaft (10) is arranged concentrically with the flange (50).

12. The fluid machine of claim 11, wherein, The first assembly gap between the crankshaft (10) and the flange (50) ranges from 0.005 mm to 0.05 mm.

13. The fluid machine of claim 12, wherein, The first assembly gap ranges from 0.01 mm to 0.03 mm.

14. The fluid machine of claim 1, wherein, The eccentric part (11) has a circular arc surface, and the central angle of the circular arc surface is greater than or equal to 180 degrees.

15. The fluid machine of claim 1, wherein, The eccentric part (11) is cylindrical.

16. The fluid machine according to claim 15, wherein The proximal end of the eccentric part (11) is flush with the outer circle of the shaft body part (12) of the crankshaft (10); or The proximal end of the eccentric part (11) protrudes from the outer circle of the shaft body part (12) of the crankshaft (10); or The proximal end of the eccentric part (11) is located on the inner side of the outer circle of the shaft body part (12) of the crankshaft (10).

17. The fluid machine of claim 1, wherein, The sliding block (40) comprises a plurality of substructures, and the plurality of substructures are spliced to surround the through hole (41).

18. The fluid machine of claim 1, wherein, The two eccentric parts (11) are arranged at intervals in the axial direction of the crankshaft (10).

19. The fluid machine of claim 1, wherein, The cross groove structure (30) has a center hole (32), the two limiting channels (31) are communicated through the center hole (32), and the hole diameter of the center hole (32) is greater than the diameter of the shaft body part (12) of the crankshaft (10).

20. The fluid machine of claim 19, wherein, The hole diameter of the center hole (32) is greater than the diameter of the eccentric part (11).

21. The fluid machine of claim 1, wherein, The projection of the sliding block (40) in the axial direction of the through hole (41) has two opposite parallel straight line segments and an arc segment connecting the ends of the two straight line segments.

22. The fluid machine of claim 1, wherein, The limiting channel (31) has a set of oppositely arranged first sliding surfaces in sliding contact with the sliding block (40), the sliding block (40) has a second sliding surface matched with the first sliding surface, the sliding block (40) has a pressing surface (42) towards the end of the limiting channel (31), the pressing surface (42) serves as the head of the sliding block (40), the two second sliding surfaces are connected through the pressing surface (42), and the pressing surface (42) faces the variable volume cavity (311).

23. The fluid machine of claim 22, wherein, The extrusion surface (42) is a curved surface, and a distance between a center of the curved surface and a center of the through hole (41) is equal to an eccentricity of the eccentric portion (11).

24. The fluid machine according to claim 23, wherein a radius of curvature of the curved surface is equal to a radius of an inner circle of the cylinder sleeve (20); or a radius of curvature of the curved surface has a difference with a radius of an inner circle of the cylinder sleeve (20), and the difference ranges from -0.05 mm to 0.025 mm.

25. The fluid machine of claim 24, wherein, the difference ranges from -0.02 mm to 0.02 mm.

26. The fluid machine of claim 22, wherein, The projected area S of the pressing surface (42) in the sliding direction of the slider (40) 滑块 The area S of the compression exhaust port of the cylinder liner (20) 排 S 滑块 / S 排 is 8 to 25.

27. The fluid machine of claim 26, wherein, S 滑块 / S 排 The value of n is 12-18.

28. The fluid machine of claim 1, wherein, The cylinder sleeve (20) has a compression intake port (21) and a compression exhaust port (22), when any one of the sliding blocks (40) is in an intake position, the compression intake port (21) is communicated with the corresponding variable volume chamber (311); when any one of the sliding blocks (40) is in an exhaust position, the corresponding variable volume chamber (311) is communicated with the compression exhaust port (22).

29. The fluid machine of claim 28, wherein, An inner wall surface of the cylinder sleeve (20) has an air suction chamber (23) which is communicated with the compression intake port (21).

30. The fluid machine of claim 29, wherein, The air suction chamber (23) extends a first preset distance along a circumference of the inner wall surface of the cylinder sleeve (20) to form an arc-shaped air suction chamber (23).

31. The fluid machine of claim 29, wherein, The air suction chamber (23) is two, and the two air suction chambers (23) are arranged in an axial direction of the cylinder sleeve (20) and are communicated with an air communication chamber (24), and the compression intake port (21) is communicated with the air suction chamber (23) through the air communication chamber (24).

32. The fluid machine of claim 31, wherein, The air communication chamber (24) extends a second preset distance along the axial direction of the cylinder sleeve (20), and at least one end of the air communication chamber (24) penetrates an axial end surface of the cylinder sleeve (20).

33. The fluid machine of claim 28, wherein, An outer wall of the cylinder sleeve (20) is provided with an exhaust chamber (25), the compression exhaust port (22) is communicated to the exhaust chamber (25) through the inner wall of the cylinder sleeve (20), and the fluid machine further comprises an exhaust valve assembly (60) which is arranged in the exhaust chamber (25) and corresponds to the compression exhaust port (22).

34. The fluid machine of claim 33, wherein, The compression exhaust port (22) is two, and the two compression exhaust ports (22) are arranged in the axial direction of the cylinder sleeve (20) and are communicated with the exhaust valve assembly (60).

35. The fluid machine of claim 34, wherein, An axial end surface of the cylinder sleeve (20) is further provided with a communication hole (26) which is communicated with the exhaust chamber (25), and the fluid machine further comprises a flange (50) which is provided with an exhaust passage (51), and the communication hole (26) is communicated with the exhaust passage (51).

36. The fluid machine of claim 33, wherein, The exhaust chamber (25) penetrates the outer wall of the cylinder sleeve (20), and the fluid machine further comprises an exhaust cover plate (70) which is connected with the cylinder sleeve (20) and seals the exhaust chamber (25).

37. The fluid machine of any one of claims 28 to 36, wherein, The fluid machine is a compressor.

38. The fluid machine of claim 1, wherein, The cylinder sleeve (20) has an expansion exhaust port and an expansion intake port, When any one of the sliding blocks (40) is in an air intake position, the expansion exhaust port is communicated with the corresponding variable volume cavity (311); When any one of the sliding blocks (40) is in an exhaust position, the corresponding variable volume cavity (311) is communicated with the expansion intake port.

39. The fluid machine of claim 38, wherein, The inner wall surface of the cylinder sleeve (20) has an expansion exhaust cavity, which is communicated with the expansion exhaust port.

40. The fluid machine of claim 39, wherein, The expansion exhaust cavity extends a first preset distance around the circumference of the inner wall surface of the cylinder sleeve (20) to form an arc-shaped expansion exhaust cavity, and the expansion exhaust cavity extends from the expansion exhaust port to the side where the expansion intake port is located, and the extension direction of the expansion exhaust cavity is the same as the rotation direction of the cross groove structure (30).

41. The fluid machine of claim 40, wherein, The expansion exhaust cavity is two, two expansion exhaust cavities are arranged in the axial direction of the cylinder sleeve (20), the cylinder sleeve (20) also has an expansion exhaust communication cavity, two expansion exhaust cavities are communicated with the expansion exhaust communication cavity, and the expansion exhaust port is communicated with the expansion exhaust cavity through the expansion exhaust communication cavity.

42. The fluid machine of claim 41, wherein, The expansion exhaust communication cavity extends a second preset distance in the axial direction of the cylinder sleeve (20), and at least one end of the expansion exhaust communication cavity penetrates the axial end surface of the cylinder sleeve (20).

43. The fluid machine of any one of claims 38-42, wherein, The fluid machine is an expander.

44. A heat exchange apparatus comprising a fluid machine, characterized by The fluid machine is the fluid machine of any one of claims 1 to 43.

45. A method of operating a fluid machine, characterized by, Comprising: The first section (121) of the crankshaft (10) rotates around the axis O0 of the first section (121), and the second section (122) of the crankshaft (10) rotates around the axis O0' of the second section (122), wherein O0 and O0' are not coincident; The axis O0 of the first section (121) is eccentrically arranged with the axis O1 of the cross groove structure (30) and the eccentric distance is fixed, and the axis O0' of the second section (122) is eccentrically arranged with the axis O1 of the cross groove structure (30) and the eccentric distance is fixed; The first sliding block (40) makes circular motion with the axis O0 of the first section (121) as the center, and the distance between the center O3 of the first sliding block (40) and the axis O0 of the first section (121) is equal to the eccentric amount of the eccentric portion (11) on the first section (121), and the eccentric amount of the first section (121) is equal to the eccentric distance between the axis O0 of the crankshaft (10) and the axis O1 of the cross groove structure (30), the crankshaft (10) rotates to drive the first sliding block (40) to make circular motion, and the first sliding block (40) interacts with the cross groove structure (30) and reciprocally slides in the limiting channel (31) of the cross groove structure (30); The second slider (40) makes a circular motion with the axis O0' of the second section (122) as the center, and the distance between the center O4 of the second slider (40) and the axis O0' of the second section (122) is equal to the eccentricity of the eccentric part (11) on the second section (122), and the eccentricity of the second section (122) is equal to the eccentric distance between the axis O0' of the second section (122) and the axis O1 of the cross groove structure (30), the crankshaft (10) rotates to drive the second slider (40) to make a circular motion, and the second slider (40) interacts with the cross groove structure (30) and reciprocates in the limiting channel (31) of the cross groove structure (30).

46. The method of operating of claim 45, wherein, The operation method adopts the principle of cross slider (40) mechanism, wherein the eccentric part (11) on the first section (121) is used as a first connecting rod L1, the eccentric part (11) on the second section (122) is used as a second connecting rod L2, and the two limiting channels (31) of the cross groove structure (30) are used as a third connecting rod L3 and a fourth connecting rod L4, respectively, wherein the lengths of the first connecting rod L1 and the second connecting rod L2 are not equal.

47. The method of operating of claim 46, wherein, The first connecting rod L1 and the second connecting rod L2 have a first included angle A, and the third connecting rod L3 and the fourth connecting rod L4 have a second included angle B, wherein the first included angle A is twice the second included angle B.

48. The method of operating of claim 47, wherein, The connecting line between the axis O0 of the first section (121), the axis O0' of the second section (122), and the axis O1 of the cross groove structure (30) is a connecting line O0 O0' O1, The first connecting rod L1 and the connecting line O0 O0' O1 have a third included angle C, and the corresponding third connecting rod L3 and the connecting line O0 O0' O1 have a fourth included angle D, wherein the third included angle C is twice the fourth included angle D; The second connecting rod L2 and the connecting line O0 O0' O1 have a fifth included angle E, and the corresponding fourth connecting rod L4 and the connecting line O0 O0' O1 have a sixth included angle F, 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.

49. The method of operating of claim 45, wherein, The operation method further comprises: The angular velocity of the rotation of the slider (40) is the same as the angular velocity of the revolution of the slider (40); The angular velocity of the revolution of the cross groove structure (30) is the same as the angular velocity of the rotation of the slider (40).

50. The method of operating of claim 45, wherein, In the process of rotation of the crankshaft (10), the crankshaft (10) rotates 2 times to complete 4 times of air intake and exhaust process.

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