CN116292303A - Fluid machine and heat exchange device with bearing - Google Patents

Abstract

The invention provides a fluid machine and heat exchange equipment with a bearing. The fluid machine includes a crankshaft, a cylinder liner, a bearing, a cross groove structure and a slider. The crankshaft has two eccentric parts; the crankshaft and the cylinder liner are arranged eccentrically and the eccentric distance is fixed. ;The bearing is arranged in the cylinder liner and the outer ring of the bearing is attached to the inner wall of the cylinder liner; the intersecting groove structure is rotatably arranged in the cylinder liner, the outer peripheral surface of the intersecting groove structure is in contact with the inner ring of the bearing, and the height of the bearing The ratio between H1 and the height H2 of the cylinder liner is greater than 0.9 and less than 1, and the two limiting channels of the cross groove structure are arranged in sequence along the axial direction of the crankshaft, and the extending direction of the limiting channel is perpendicular to the axial direction of the crankshaft; the slider There are through holes, and there are two sliders, and the two eccentric parts correspondingly extend into the two through holes of the two sliders, and the two sliders are correspondingly slidably arranged in the two position-limiting passages to form variable volume chambers. The invention solves the problems of low energy efficiency and high noise of the compressor in the prior art.

Description

Fluid machinery and heat exchange equipment with bearings

technical field

The invention relates to the technical field of heat exchange systems, in particular to a fluid machine and heat exchange equipment with bearings.

Background technique

Fluid machines in the prior art include compressors, expanders, and the like. Take compressors as an example.

According to the national energy-saving and environmental protection policy and consumers' requirements for air-conditioning comfort, the air-conditioning industry has been pursuing high efficiency and low noise. As the heart of the air conditioner, the compressor has a direct impact on the energy efficiency and noise level of the air conditioner. As the mainstream household air-conditioning compressor, the rolling rotor compressor has been relatively mature after nearly a hundred years of development. Due to the limitation of structural principles, the optimization space is limited. In order to achieve a major breakthrough, it is necessary to innovate from the structural principle.

Therefore, it is urgent to propose a compressor with the characteristics of high energy efficiency and low noise.

Contents of the invention

The main purpose of the present invention is to provide a fluid machine and heat exchange equipment with bearings, so as to solve the problems of low energy efficiency and high noise of compressors in the prior art.

In order to achieve the above object, according to one aspect of the present invention, a fluid machine with a bearing is provided, including a crankshaft, a cylinder liner, a bearing, a cross groove structure and a slider, wherein the crankshaft is provided with two eccentric parts along its axial direction ; The crankshaft and the cylinder liner are set eccentrically and the eccentric distance is fixed; the bearing is set in the cylinder liner and the outer ring of the bearing is attached to the inner wall of the cylinder liner; The inner ring of the bearing fits closely, and the ratio between the height H1 of the bearing and the height H2 of the cylinder liner is greater than 0.9 and less than 1. The cross groove structure has two limiting channels, and the two limiting channels are sequentially along the crankshaft axis Setting, the extension direction of the limiting channel is perpendicular to the axial direction of the crankshaft; the slider has a through hole, and there are two sliders, and the two eccentric parts correspondingly extend into the two through holes of the two sliders, and the two sliders correspond to The sliding is set in the two limiting channels and forms a variable volume chamber, which is located in the sliding direction of the slider. The crankshaft rotates to drive the slider to reciprocate in the limiting channel and interact with the cross groove structure, so that the cross Groove structure, the slider rotates in the cylinder liner.

Further, the height H1 of the bearing and the height H2 of the cylinder liner satisfy: 0.003mm≤H2-H1≤0.1mm.

Further, there is a phase difference of a first angle A between the two eccentric parts, the eccentric amounts of the two eccentric parts are equal, and there is a phase difference of a second angle B between the extension directions of the two limiting channels, wherein , the first angle A is twice the second angle B.

Further, the eccentricity of the eccentric part is equal to the assembly eccentricity of the crankshaft and the cylinder liner.

Further, both ends of the limiting channel penetrate to the outer peripheral surface of the intersecting groove structure.

Further, the two sliders are arranged concentrically with the two eccentric parts respectively, and the sliders make circular motions around the eccentric parts, and there is a first rotation gap between the wall of the through hole and the eccentric parts, and the range of the first rotation gap is 0.005mm ~0.05mm.

Further, the outer circumference of the cylinder liner has a circumferential protruding ring, and a plurality of elongated holes arranged at intervals are arranged on the circumferential protruding ring.

Further, the first included angle A is 160°-200°; the second included angle B is 80°-100°.

Further, the fluid machine further includes a flange, the flange is arranged on the axial end of the cylinder liner, and the crankshaft is arranged concentrically with the flange.

Further, there is a first assembly gap between the crankshaft and the flange, and the range of the first assembly gap is 0.005mm-0.05mm.

Further, the range of the first assembly gap is 0.01-0.03 mm.

Further, the eccentric part has an arc surface, and the central angle of the arc surface is greater than or equal to 180 degrees.

Further, the eccentric part is cylindrical.

Further, the proximal end of the eccentric portion is flush with the outer circle of the shaft portion of the crankshaft; or, the proximal end of the eccentric portion protrudes from the outer circle of the shaft portion of the crankshaft; or, the proximal end of the eccentric portion is located at the shaft body of the crankshaft The inner side of the outer circle of the part.

Further, the slider includes a plurality of substructures, and the plurality of substructures are spliced to form a through hole.

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

Further, the intersecting groove structure has a central hole through which the two limiting passages communicate, and the diameter of the central hole is larger than the diameter of the crankshaft shaft body.

Further, the diameter of the central hole is larger than the diameter of the eccentric part.

Further, the projection of the slider on the axial direction of the through hole has two relatively parallel straight line segments and an arc segment connecting ends of the two straight line segments.

Further, the slider has an extrusion surface facing the end of the limiting channel, the extrusion surface serves as the head of the slider, and the extrusion surface faces the variable volume chamber.

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

Further, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner; or, there is a difference between the radius of curvature of the arc surface and the radius of the inner circle of the cylinder liner, and the difference ranges from -0.05mm to 0.025mm.

Further, the range of the difference is -0.02-0.02mm.

Further, the projected area S of the extrusion surface in the sliding direction of the slider S is the area between the compression and exhaust ports of _{the slider} and the cylinder liner, which satisfies between the S _rows : the value of the S _slider /S _row is 8-25.

Further, the value of the S _slider /S _row is 12-18.

Further, the fluid machine includes two flanges, the two flanges are respectively assembled on the axial ends of the cylinder liner, the two flanges are respectively provided with air intake passages, and the two air intake passages are connected with the two limit passages respectively. The two flanges are respectively provided with exhaust passages, and there is a phase difference between the intake passage and the exhaust passage on the same flange.

Further, the intake passage includes a first intake passage section and a second intake passage section connected in sequence, the first intake passage section extends radially along the flange, and the second intake passage section extends along the axis of the flange. to extend.

Further, an exhaust groove is provided on the end surface of the flange away from the cylinder liner, and an exhaust communication port is provided at the bottom of the exhaust groove and communicates with the limiting channel, and the exhaust communication port extends along the axial direction of the flange.

Further, the end of the intake passage is an intake communication port, and the initial end of the exhaust passage is an exhaust communication port. When any slider is at the intake position, the intake communication port is connected to the corresponding variable volume cavity; When any slider is in the exhaust position, the corresponding variable volume chamber is connected to the exhaust communication port.

Further, the fluid machine is a compressor.

Further, the end of the intake passage is an intake communication port, and the initial end of the exhaust passage is an exhaust communication port. When any slider is at the intake position, the exhaust communication port is in communication with the corresponding variable volume chamber; When any slider is in the exhaust position, the corresponding variable volume cavity is connected to the air intake port.

Further, the fluid machine is an expander.

According to another aspect of the present invention, a heat exchange device is provided, including a fluid machine, and the fluid machine is the above-mentioned fluid machine.

Applying the technical solution of the present invention, by setting the intersecting groove structure into a structural form with two limiting channels, and correspondingly setting up two sliders, the two eccentric parts of the crankshaft correspondingly extend into the two through holes of the two sliders At the same time, the two sliders are correspondingly slidably arranged in the two limiting passages and form a variable volume cavity, so that when one of the two sliders is at the dead point, that is, the same as the slider at the dead point The driving torque of the eccentric part corresponding to the block is 0, and the slider at the dead point cannot continue to rotate, and at this time, the driving torque of the other eccentric part driving the corresponding slider is the maximum value, Ensure that the eccentric part with the maximum driving torque can normally drive the corresponding slider to rotate, thereby driving the cross groove structure to rotate through the slider, and then driving the slider at the dead point to continue to rotate through the cross groove structure, realizing fluid flow The stable operation of the machine avoids the dead point position of the motion mechanism, improves the motion reliability of the fluid machine, and ensures the work reliability of the heat exchange equipment.

In addition, by arranging the bearing in the cylinder liner, the outer ring of the bearing is attached to the inner wall of the cylinder liner, and the ratio between the height H1 of the bearing and the height H2 of the cylinder liner is greater than 0.9 and less than 1, so that the cross groove structure The entire outer circle in the axial direction is supported by bearings to reduce friction, so that the sliding friction between the circumferential outer surface of the cross groove structure and the inner wall of the cylinder liner changes into the rolling friction between the circumferential outer surface of the cross groove structure and the bearing, reducing The mechanical friction power consumption is calculated, wherein, the inner ring of the bearing cooperates with the cross groove structure, and the inner ring of the bearing cooperates with the inner wall of the cylinder liner.

Further, since the fluid machine provided by the present application can run stably, that is, the energy efficiency of the compressor is high and the noise is low, thereby ensuring the reliability of the heat exchange equipment.

Description of drawings

The accompanying drawings constituting a part of the present application are used to provide a further understanding of the present invention, and the schematic embodiments and descriptions of the present invention are used to explain the present invention, and do not constitute an improper limitation of the present invention. In the attached picture:

Fig. 1 shows a schematic diagram of the mechanism principle of compressor operation according to an alternative embodiment of the present invention;

Fig. 2 shows a schematic diagram of the principle of operation of the compressor in Fig. 1;

Fig. 3 shows a schematic diagram of the internal structure of a compressor according to an alternative embodiment of the present invention;

Fig. 4 shows a schematic structural view of the pump body assembly of the compressor in Fig. 3;

Figure 5 shows a schematic diagram of the exploded structure of the pump body assembly in Figure 4;

Fig. 6 shows a schematic diagram of the comparative structure of the height H1 of the bearing in Fig. 5 and the height H2 of the cylinder liner;

Fig. 7 shows the structural representation of crankshaft in Fig. 5, intersecting groove structure, slide block when being in assembled state;

Fig. 8 shows the schematic cross-sectional structural view of the crankshaft, intersecting groove structure, and slide block in Fig. 7;

Fig. 9 shows a structural schematic diagram of the shaft body part of the crankshaft in Fig. 5 and the eccentricity of the two eccentric parts;

Fig. 10 shows a schematic cross-sectional structural view of the assembly eccentricity of the crankshaft and cylinder liner in Fig. 5;

Fig. 11 shows a schematic structural view of the cylinder liner and the lower flange in Fig. 5 when they are in an exploded state;

Fig. 12 shows a schematic structural view of the eccentricity between the cylinder liner and the lower flange in Fig. 11;

Fig. 13 shows a schematic structural view of the slider in Fig. 5 in the axial direction of the through hole;

Fig. 14 shows a schematic structural view of the intake channel and the exhaust channel of the upper flange in Fig. 5;

Fig. 15 shows a schematic structural view of the intake channel and the exhaust channel of the lower flange in Fig. 5;

Fig. 16 shows a schematic view of the structure when the upper flange and the cylinder liner in Fig. 14 are in an assembled state;

Fig. 17 shows a schematic view of the structure of the I-I perspective in Fig. 16;

Figure 18 shows a schematic view of the structure of the II-II perspective in Figure 17, in this figure, the compressor is in the suction state;

Figure 19 shows a schematic view of the structure of the II-II perspective in Figure 17, in this figure, the compressor is in a compressed gas state;

Fig. 20 shows a schematic view of the structure of II-II perspective in Fig. 17, in this figure, the compressor is in the exhaust state;

Figure 21 shows a schematic diagram of the exploded structure of the pump body assembly with bearings in Figure 4;

Fig. 22 shows a schematic structural view of the intersecting groove structure and the slider according to an alternative embodiment of the present invention;

Fig. 23 shows a schematic structural view of the intersecting groove structure and the slider according to an alternative embodiment of the present invention;

Fig. 24 shows a schematic structural diagram of a cross groove structure and a slider according to an alternative embodiment of the present invention;

Fig. 25 shows a schematic structural diagram of a cross groove structure and a slider according to an alternative embodiment of the present invention;

Fig. 26 shows a schematic diagram of the mechanism principle of compressor operation in the prior art;

Fig. 27 shows a schematic diagram of the mechanism principle of the improved compressor operation in the prior art;

Fig. 28 shows a schematic diagram of the operating mechanism of the compressor in Fig. 27. In this figure, the force arm of the drive shaft driving the slider to rotate is shown;

Fig. 29 shows a schematic diagram of the operating mechanism of the compressor in Fig. 27. In this figure, the center of the limiting groove structure coincides with the center of the eccentric part.

Wherein, the above-mentioned accompanying drawings include the following reference signs:

10. Crankshaft; 11. Eccentric part; 12. Shaft part;

20, cylinder liner; 28, circumferential convex ring; 281, long hole;

30. Cross groove structure; 31. Limiting channel; 311. Variable volume chamber; 32. Center hole;

40. slider; 41. through hole; 42. extrusion surface;

50, flange; 51, exhaust channel; 52, upper flange; 53, lower flange; 54, air intake channel; 541, first air intake channel section; 542, second air intake channel section; 55, row Air groove; 551, exhaust communication port;

80. Dispenser component; 81. Housing assembly; 82. Motor assembly; 83. Pump body assembly; 84. Upper cover assembly; 85. Lower cover assembly;

90. Fasteners;

200, bearing.

Detailed ways

The following will clearly and completely describe the technical solutions in the embodiments of the present invention with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only some of the embodiments of the present invention, not all of them. The following description of at least one exemplary embodiment is merely illustrative in nature and in no way taken as limiting the invention, its application or uses. Based on the embodiments of the present invention, all other embodiments obtained by persons of ordinary skill in the art without creative efforts fall within the protection scope of the present invention.

In the prior art, as shown in Figure 26, a compressor operating mechanism principle is proposed based on the cross slider mechanism, that is, point _O1 is used as the center of the cylinder, point _O2 is used as the center of the drive shaft, and point _O3 is used as the slider In the center, the cylinder and the drive shaft are set eccentrically, wherein the slider center O ₃ makes a circular motion on a circle with a diameter of O ₁ O ₂ .

In the above operating mechanism principle, the cylinder center O ₁ and the drive shaft center O ₂ are used as the two rotation centers of the motion mechanism, and at the same time, the midpoint O ₀ of the line segment O ₁ O ₂ is used as the virtual center of the slider center O ₃ , so that the slider While the block reciprocates relative to the cylinder, the slider also reciprocates relative to the drive shaft.

Since the midpoint O ₀ of the line segment O ₁ O ₂ is the virtual center, it is impossible to set up a balance system, resulting in the deterioration of the high-frequency vibration characteristics of the compressor. Based on the principle of the above-mentioned operating mechanism, as shown in Figure 27, a The motion mechanism with O ₀ as the drive shaft center, that is, the cylinder center O ₁ and the drive shaft center O ₀ as the two rotation centers of the motion mechanism, the drive shaft has an eccentric portion, the slider and the eccentric portion are coaxially arranged, and the drive shaft and The assembly eccentricity of the cylinder is equal to the eccentricity of the eccentric part, so that the slider center _O3 makes a circular motion with the drive shaft center _O0 as the center and _O1O0 as the radius _.

Correspondingly, a set of operating mechanisms is proposed, including a cylinder, a limit groove structure, a slider and a drive shaft, wherein the limit groove structure is rotatably arranged in the cylinder, and the cylinder and the limit groove structure are coaxially arranged, that is, The center _O1 of the cylinder is also the center of the limit groove structure, the slider reciprocates relative to the limit groove structure, the slider is coaxially assembled with the eccentric portion of the drive shaft, and the slider moves circularly around the shaft part of the drive shaft, specifically The movement process is: the drive shaft rotates, driving the slider to revolve around the center of the shaft part of the drive shaft, the slider rotates relative to the eccentric part at the same time, and the slider reciprocates in the limit groove of the limit groove structure, and pushes the limit Bitslot structure rotation.

However, as shown in Figure 28, the length of the force arm L that the drive shaft drives the slider to rotate is L=2e×cosθ×cosθ, where e is the eccentricity of the eccentric part, and θ is the line connecting O ₁ O ₀ and the slider The angle between the sliding directions in the limit slot.

As shown in Figure 29, when the center of the cylinder O ₁ (that is, the center of the limit groove structure) coincides with the center of the eccentric part, the resultant force of the driving force of the drive shaft passes through the center of the limit groove structure, that is, it is applied to the limit groove structure. The torque on the groove structure is zero, and the limit groove structure cannot rotate. At this time, the motion mechanism is at the dead point and cannot drive the slider to rotate.

Based on this, this application proposes a brand-new mechanism principle of a cross-slot structure with two limiting channels and double sliders, and builds a brand-new compressor based on this principle, which has high energy efficiency, low noise Small features, the following takes the compressor as an example, and specifically introduces the compressor based on the cross-groove structure with two limiting channels and double sliders.

In order to solve the problems of low energy efficiency and high noise of compressors in the prior art, the present invention provides a fluid machine with bearings and heat exchange equipment, wherein the heat exchange equipment includes the fluid machine described below.

The fluid machine with bearing in the present invention comprises crankshaft 10, cylinder liner 20, bearing 200, intersecting groove structure 30 and slide block 40, wherein, crankshaft 10 is provided with two eccentric parts 11 along its axial direction; 20 is set eccentrically and the eccentric distance is fixed; the bearing 200 is set in the cylinder liner 20 and the outer ring of the bearing 200 is attached to the inner wall of the cylinder liner 20; the cross groove structure 30 is rotatably set in the cylinder liner 20, and the The outer peripheral surface fits the inner ring of the bearing 200, and the ratio between the height H1 of the bearing 200 and the height H2 of the cylinder liner 20 is greater than 0.9 and less than 1, and the intersecting groove structure 30 has two limiting channels 31, two limiting channels The channel 31 is arranged in sequence along the axial direction of the crankshaft 10, and the extension direction of the limiting channel 31 is perpendicular to the axial direction of the crankshaft 10; the slider 40 has a through hole 41, and there are two sliders 40, and the two eccentric parts 11 extend into the corresponding In the two through holes 41 of the two sliders 40, the two sliders 40 are correspondingly slidably arranged in the two limiting passages 31 and form a variable volume cavity 311. The variable volume cavity 311 is located in the sliding direction of the slider 40, and the crankshaft 10 rotates to drive the slider 40 to reciprocally slide in the limiting channel 31 and at the same time interact with the intersecting groove structure 30 , so that the intersecting groove structure 30 and the slider 40 rotate in the cylinder liner 20 .

By setting the intersecting groove structure 30 into a structural form with two limiting channels 31 and correspondingly setting up two sliders 40, the two eccentric parts 11 of the crankshaft extend into the two through holes 41 of the two sliders 40 correspondingly. , at the same time, the two slide blocks 40 are correspondingly slidably arranged in the two limiting passages 31 and form a variable volume chamber 311, so that when one of the two slide blocks 40 is at the dead point position, that is, the same as being at the dead point position The driving torque of the eccentric part 11 corresponding to the slider 40 at the position is 0, and the slider 40 at the dead point cannot continue to rotate, and at this time the other eccentric part 11 of the two eccentric parts 11 drives the corresponding slider The driving torque of 40 is the maximum value, ensuring that the eccentric part 11 with the maximum driving torque can normally drive the corresponding slider 40 to rotate, thereby driving the cross groove structure 30 to rotate through the slider 40, and then driving the cross groove structure 30 to rotate The slider 40 at the dead point continues to rotate, realizing the stable operation of the fluid machine, avoiding the dead point of the motion mechanism, improving the motion reliability of the fluid machine, and ensuring the working reliability of the heat exchange equipment.

In addition, by arranging the bearing 200 in the cylinder liner 20 and the outer ring of the bearing 200 is attached to the inner wall of the cylinder liner 20, the ratio between the height H1 of the bearing 200 and the height H2 of the cylinder liner 20 is defined to be greater than 0.9 and less than 1 In this way, the entire outer circle of the intersecting groove structure 30 in the axial direction is supported by the bearing 200 to reduce friction, so that the sliding friction between the circumferential outer surface of the intersecting groove structure 30 and the inner wall of the cylinder liner 20 changes to that of the intersecting groove structure 30. The rolling friction between the circumferential outer surface and the bearing 200 reduces mechanical friction power consumption, wherein the inner ring of the bearing 200 cooperates with the intersecting groove structure 30 , and the inner ring of the bearing 200 cooperates with the inner wall of the cylinder liner 20 .

Further, since the fluid machine provided by the present application can run stably, that is, the energy efficiency of the compressor is high and the noise is low, thereby ensuring the reliability of the heat exchange equipment.

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

As shown in Figures 1 and 2, when the above-mentioned fluid machine is in operation, the crankshaft 10 rotates around the axis O ₀ of the crankshaft 10; the intersecting groove structure 30 revolves around the axis O ₀ of the crankshaft 10, and the axis O ₀ Set eccentrically with the axis O ₁ of the intersecting groove structure 30 and the eccentric distance is fixed; the first slider 40 makes a circular motion with the axis O ₀ of the crankshaft 10 as the center of a circle, and the center O ₃ of the first slider 40 is aligned with the crankshaft The distance between the axis O0 of ₁₀ is equal to the eccentricity of the first eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentricity between the axis O0 of the crankshaft ₁₀ and the axis O1 of the intersecting groove structure ₃₀ distance, the crankshaft 10 rotates to drive the first slider 40 to make a circular motion, and the first slider 40 interacts with the intersecting groove structure 30 and slides reciprocally in the limiting channel 31 of the intersecting groove structure 30; The block 40 moves in a circle with the axis O0 of the crankshaft ₁₀ as the center, and the distance between the center _O4 of the second slider 40 and the axis _O0 of the crankshaft 10 is equal to the second eccentric part 11 corresponding to the crankshaft 10 eccentricity, and the eccentricity is equal to the eccentric distance between the axis O ₀ of the crankshaft 10 and the axis O ₁ of the intersecting groove structure 30, the crankshaft 10 rotates to drive the second slider 40 to do circular motion, and the second The slider 40 interacts with the intersecting groove structure 30 and slides reciprocally in the limiting channel 31 of the intersecting groove structure 30 .

The fluid machine operated as described above constitutes an Oldham slider mechanism, and the operation method adopts the principle of the Oldham slider mechanism, wherein the two eccentric parts 11 of the crankshaft 10 serve as the first connecting rod _L1 and the second connecting rod _L2 respectively. , the two limiting channels 31 of the intersecting groove structure 30 are respectively used as the third link L ₃ and the fourth link L ₄ , and the lengths of the first link L ₁ and the second link L ₂ are equal (please refer to FIG. 1 ).

As shown in Figure 1, there is a first included angle A between the first link _L1 and the second link _L2 , and there is a second included angle B between the third link _L3 and the fourth link _L4 , Wherein, the first included angle A is twice the second included angle B.

As shown in Figure 2, the line connecting the axis O ₀ of the crankshaft 10 and the axis O ₁ of the intersecting groove structure 30 is the line O ₀ O ₁ , and the line between the first connecting rod L ₁ and the line O ₀ O ₁ There is a third included angle C between them, and there is a fourth included angle D between the corresponding third link L ₃ and the connecting line O ₀ O ₁ , wherein the third included angle C is twice the fourth included angle D; There is a fifth included angle E between the second connecting rod L ₂ and the connecting line O ₀ O ₁ , and there is a sixth included angle F between the corresponding fourth connecting rod L ₄ and the connecting line O ₀ O ₁ , wherein the fifth included angle The angle E is twice the sixth angle F; the sum of the third angle C and the fifth angle E is the first angle A, and the sum of the fourth angle D and the sixth angle F is the second angle b.

Further, the operation method also includes that the rotational angular velocity of the slider 40 relative to the eccentric portion 11 is the same as the revolution angular velocity of the slider 40 around the axis O ₀ of the crankshaft ₁₀ ; This is the same as the rotational angular velocity of the slider 40 relative to the eccentric portion 11 .

Specifically, the axis _O0 of the crankshaft 10 corresponds to the rotation center of the first connecting rod _L1 and the second connecting rod _L2 , and the axis O1 of the intersecting groove structure ₃₀ corresponds to the third connecting rod L3 and the fourth connecting rod _L3 . The rotation center of the connecting rod _L4 ; the two eccentric parts 11 of the crankshaft 10 are respectively used as the first connecting rod _L1 and the second connecting rod _L2 , and the two limiting channels 31 of the intersecting groove structure 30 are respectively used as the third connecting rod L ₃ and the fourth connecting rod L ₄ , and the lengths of the first connecting rod L ₁ and the second connecting rod L ₂ are equal, so that when the crankshaft 10 rotates, the eccentric part 11 on the crankshaft 10 drives the corresponding slider 40 around the crankshaft The axis O0 of ₁₀ revolves, and the slider 40 can rotate relative to the eccentric part 11 at the same time, and the relative rotation speed of the two is the same, because the first slider 40 and the second slider 40 are respectively in two corresponding limits Reciprocating movement in the position channel 31, and drives the intersecting groove structure 30 to make a circular motion, limited by the two limiting channels 31 of the intersecting groove structure 30, the moving direction of the two sliders 40 always has the phase of the second included angle B difference, when one of the two sliders 40 is at the dead center position, the eccentric portion 11 for driving the other of the two sliders 40 has the largest driving torque, and the eccentric portion 11 with the largest driving torque can Normally drive the corresponding slider 40 to rotate, so that the cross groove structure 30 is driven to rotate by the slider 40, and then the slider 40 at the dead point is driven by the cross groove structure 30 to continue to rotate, realizing the stable operation of the fluid machine. The dead point position of the motion mechanism is avoided, and the motion reliability of the fluid machinery is improved, thereby ensuring the working reliability of the heat exchange equipment.

It should be noted that, in this application, the maximum moment arm of the driving torque of the eccentric portion 11 is 2e.

Under this movement method, the running track of the slider 40 is a circle, and the circle takes the axis O ₀ of the crankshaft 10 as the center and the connecting line O ₀ O ₁ as the radius.

It should be noted that, in this application, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 times to complete 4 intake and exhaust processes.

An optional implementation 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 structural features.

Optionally, the bearing 200 is a cage needle roller + inner ring bearing, or a ball bearing, or other bearings capable of realizing this function.

As shown in FIG. 6 , the height H1 of the bearing 200 and the height H2 of the cylinder liner 20 satisfy: 0.003mm≤H2-H1≤0.1mm. In this way, by optimizing the difference between the height H1 of the bearing 200 and the height H2 of the cylinder liner 20, the inclination phenomenon of the intersecting groove structure 30 is effectively prevented, ensuring good lubrication between the intersecting groove structure 30 and the cylinder liner 20 , thereby reducing the mechanical friction power consumption between the fork groove structure 30 and the cylinder liner 20, which is beneficial to improving the performance of the compressor, thereby improving the operation reliability of the compressor.

It should be noted that, in this embodiment, since the height H1 of the bearing 200 is similar to the height H2 of the cylinder liner 20, and in order to ensure the reliability of the support of the bearing 200 to the intersecting groove structure 30, no suction and discharge are provided in the radial direction of the bearing 200. The air port, specifically, as shown in Figure 10, the fluid machine includes two flanges 50, the two flanges 50 are respectively assembled on the axial ends of the cylinder liner 20, and the two flanges 50 are respectively provided with air intake passages 54, the two intake passages 54 communicate with the two limiting passages 31 respectively, and the two flanges 50 are respectively provided with exhaust passages 51, the same flange 50 on the intake passage 54 and the exhaust passage 51 There is a phase difference between them. In this way, while the integrity of the bearing 200 is ensured, the reliability of the intake and exhaust of the cylinder liner 20 is ensured.

As shown in Fig. 1, there is a phase difference of a first angle A between the two eccentric parts 11, the eccentric amounts of the two eccentric parts 11 are equal, and there is a second included angle between the extension directions of the two limiting channels 31 The phase difference of B, wherein, the first angle A is twice the second angle B.

As shown in Figure 3 to Figure 21, the fluid machine also includes a flange 50, the flange 50 is arranged on the axial end of the cylinder liner 20, the crankshaft 10 is concentrically arranged with the flange 50, and the cross groove structure 30 is concentric with the cylinder liner 20. shaft setting, the assembly eccentricity of the crankshaft 10 and the intersecting groove structure 30 is determined by the relative positional relationship between the flange 50 and the cylinder liner 20, wherein the flange 50 is fixed on the cylinder liner 20 by a fastener 90, and the axis of the flange 50 The relative position of the axis of the inner ring of the cylinder liner 20 is controlled by the alignment of the flange 50, and the relative position of the axis of the flange 50 and the axis of the inner ring of the cylinder liner 20 determines the axis of the crankshaft 10 and the cross groove structure 30 The relative position of the shaft center, the essence of aligning through the flange 50 is to make the eccentricity of the eccentric part 11 equal to the assembly eccentricity of the crankshaft 10 and the cylinder liner 20 .

Specifically, as shown in FIG. 9, the eccentricity of the two eccentric parts 11 is equal to e, and as shown in FIG. 20 are coaxially arranged, the assembly eccentricity between the crankshaft 10 and the intersecting groove structure 30 is the assembly eccentricity between the crankshaft 10 and the cylinder liner 20), and the flange 50 includes an upper flange 52 and a lower flange 53, as shown in Figure 12 As shown, the distance between the axis of the inner ring of the cylinder liner 20 and the axis of the inner ring of the lower flange 53 is e, that is, equal to the eccentricity of the eccentric portion 11 .

Optionally, there is a first assembly gap between the crankshaft 10 and the flange 50, and the range of the first assembly gap is 0.005mm˜0.05mm.

Preferably, the range of the first assembly gap is 0.01-0.03mm.

As shown in FIG. 4 , FIG. 5 , and FIG. 7 to FIG. 10 , the shaft part 12 of the crankshaft 10 is integrally formed, and the shaft part 12 has only one shaft center. In this way, the one-time molding of the shaft part 12 is facilitated, thereby reducing the difficulty of manufacturing the shaft part 12 .

It should be noted that, in an unillustrated embodiment of the present application, the shaft portion 12 of the crankshaft 10 includes a first section and a second section connected along its axial direction, the first section and the second section are arranged coaxially, Two eccentric portions 11 are respectively arranged on the first segment and the second segment.

Optionally, the first segment is detachably connected to the second segment. In this way, ease of assembly and disassembly of the crankshaft 10 is ensured.

As shown in FIG. 4 , FIG. 5 , and FIG. 7 to FIG. 10 , the shaft part 12 of the crankshaft 10 and the eccentric part 11 are integrally formed. In this way, one-shot forming of the crankshaft 10 is facilitated, thereby reducing the difficulty of manufacturing the crankshaft 10 .

It should be noted that, in an unillustrated embodiment of the present application, the shaft portion 12 of the crankshaft 10 is detachably connected to the eccentric portion 11 . In this way, the installation and removal of the eccentric portion 11 is facilitated.

As shown in FIG. 5 , both ends of the limiting channel 31 penetrate to the outer peripheral surface of the intersecting groove structure 30 . In this way, it is beneficial to reduce the manufacturing difficulty of the intersecting groove structure 30 .

Optionally, the two sliders 40 are arranged concentrically with the two eccentric parts 11 respectively, the sliders 40 make circular motions around the eccentric parts 11, there is a first rotation gap between the hole wall of the through hole 41 and the eccentric parts 11, the first The range of the rotation clearance is 0.005mm～0.05mm.

As shown in Fig. 4, Fig. 5, Fig. 10 to Fig. 12, Fig. 16 and Fig. 17, the outer periphery of the cylinder liner 20 has a circumferential protruding ring 28, and a plurality of strips arranged at intervals are arranged on the circumferential protruding ring 28. Hole 281. In this way, the elongated hole 281 plays the role of oil return in the environment space.

It should be noted that, in the present application, the first included angle A is 160°-200°; the second included angle B is 80°-100°. In this way, it only needs to satisfy the relationship that the first included angle A is twice the second included angle B.

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

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

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

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

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

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

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

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

It should be noted that, in the present 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. In this way, it is ensured that the arc surface of the eccentric portion 11 can exert an effective driving force on the slider 40 , thereby ensuring the reliability of the movement of the slider 40 .

As shown in Fig. 4, Fig. 5, Fig. 7 to Fig. 10, the eccentric portion 11 is cylindrical.

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

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

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

It should be noted that, in an unillustrated embodiment of the present application, the slider 40 includes a plurality of substructures, and the plurality of substructures are spliced to form a through hole 41 .

As shown in FIG. 4 , FIG. 5 , and FIG. 7 to FIG. 10 , the two eccentric portions 11 are arranged at intervals in the axial direction of the crankshaft 10 . In this way, during the process of assembling the crankshaft 10 , the cylinder liner 20 and the two sliders 40 , ensuring the distance between the two eccentric parts 11 can provide an assembly space for the cylinder liner 20 to ensure the convenience of assembly.

As shown in FIG. 5 , the intersecting groove structure 30 has a central hole 32 through which the two limiting passages 31 communicate. The diameter of the central hole 32 is larger than the diameter of the shaft portion 12 of the crankshaft 10 . In this way, it is ensured that the crankshaft 10 can pass through the central hole 32 smoothly.

Optionally, the diameter of the central hole 32 is larger than the diameter of the eccentric portion 11 . In this way, it is ensured that the eccentric portion 11 of the crankshaft 10 can smoothly pass through the central hole 32 .

As shown in FIG. 13 , the axial projection of the slider 40 on the through hole 41 has two relatively parallel straight line segments and an arc segment connecting ends of the two straight line segments. The limiting channel 31 has a set of first sliding surfaces oppositely disposed in sliding contact with the slider 40 , the sliding block 40 has a second sliding surface cooperating with the first sliding surfaces, and the sliding block 40 has a The extrusion surface 42 at the end of the slider 40 is used as the head of the slider 40, and the two second sliding surfaces are connected by the extrusion surface 42, and the extrusion surface 42 faces the variable volume chamber 311. In this way, the projection of the second sliding surface of the slider 40 in the axial direction of the through hole 41 is a straight line segment, and at the same time, the projection of the extrusion surface 42 of the slider 40 in the axial direction of the through hole 41 is an arc segment.

Specifically, the extrusion surface 42 is an arc surface, and the distance between the arc center of the arc surface and the center of the through hole 41 is equal to the eccentricity of the eccentric portion 11 . In Fig. 13, the center of the through hole 41 of the slider 40 is the O _slider , and the distance between the arc centers of the two arc surfaces and the center of the through hole 41 is e, that is, the eccentricity of the eccentric portion 11, as shown in Fig. 13 The dotted line of X indicates the circle where the arc centers of the two arc surfaces are located.

It should be noted that, in this application, as shown in FIG. 5 , the slider 40 has an extrusion surface 42 facing the end of the limiting passage 31, the extrusion surface 42 serves as the head of the slider 40, and the extrusion surface 42 Towards the variable volume cavity 311 .

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

Optionally, there is a difference between the radius of curvature of the arc surface and the radius of the inner circle of the cylinder liner 20, and the difference ranges from -0.05mm to 0.025mm.

Preferably, the difference ranges from -0.02 to 0.02mm.

It should be noted that, in this application, _{the projected area S of the extrusion surface 42 in the sliding direction of the slider 40 satisfies: S slider / S The row} value is 8-25.

Preferably, the value of S _slider /S _row is 12-18.

It should be noted that the fluid machine shown in this embodiment is a compressor. As shown in FIG. The lower cover assembly 85, wherein the liquid separator part 80 is arranged on the outside of the housing assembly 81, the upper cover assembly 84 is assembled on the upper end of the housing assembly 81, the lower cover assembly 85 is assembled on the lower end of the housing assembly 81, and the motor assembly 82 Both the motor assembly 82 and the pump body assembly 83 are located inside the housing assembly 81 , wherein the motor assembly 82 is located above the pump body assembly 83 , or the motor assembly 82 is located below the pump body assembly 83 . The pump body assembly 83 of the compressor includes the crankshaft 10 , the cylinder liner 20 , the intersecting groove structure 30 , the slider 40 , the upper flange 52 and the lower flange 53 .

Optionally, the above-mentioned components are connected by means of welding, shrink fitting, or cold pressing.

The assembly process of the entire pump body assembly 83 is as follows: the lower flange 53 is fixed on the cylinder liner 20, the two sliders 40 are respectively placed in the corresponding two limiting passages 31, and the two eccentric parts 11 of the crankshaft 10 respectively extend into the In the two through holes 41 of the corresponding two sliders 40, the assembled crankshaft 10, the cross groove structure 30 and the two sliders 40 are placed in the cylinder liner 20, and one end of the crankshaft 10 is installed on the lower flange 53 , the other end of the crankshaft 10 is set through the upper flange 52 , see FIG. 4 and FIG. 5 for details.

It should be noted that, in this embodiment, the closed space surrounded by the slider 40, the limiting channel 31, the cylinder liner 20 and the upper flange 52 (or the lower flange 53) is the variable volume chamber 311, and the pump body assembly 83 has four variable volume chambers 311 in total. During the rotation of the crankshaft 10, the crankshaft 10 rotates 2 revolutions, and a single variable volume chamber 311 completes one intake and exhaust process. For the compressor, the crankshaft 10 rotates 2 revolutions, totaling Complete 4 suction and exhaust processes.

As shown in Figures 18 to 20, during the reciprocating movement of the slider 40 in the limiting channel 31, it rotates relative to the cylinder liner 20 at the same time. In Figure 18, the slider 40 rotates clockwise from 0° to 180° During the process of increasing the variable volume cavity 311, the variable volume cavity 311 communicates with the suction cavity of the cylinder liner 20. When the slider 40 rotates to 180 degrees, the volume of the variable volume cavity 311 reaches At this time, the variable volume cavity 311 is separated from the suction cavity, thereby completing the suction operation. In Fig. 19 and Fig. 20, the sliding block 40 continues to rotate from 180° to 360° in the clockwise direction. The volume chamber 311 decreases, and the slider 40 compresses the gas in the variable volume chamber 311. When the slider 40 rotates to the point where the variable volume chamber 311 communicates with the compression exhaust port 22, and when the gas in the variable volume chamber 311 reaches the exhaust When the air pressure is high, the exhaust valve of the exhaust valve assembly opens to start the exhaust operation until the compression ends and enters the next cycle.

As shown in FIGS. 18 to 20 , the slider 40 rotates once, and the corresponding crankshaft 10 rotates twice.

As shown in Figure 4, Figure 10, Figure 14 to Figure 20, the fluid machine includes two flanges 50, the flange 50 includes an upper flange 52 and a lower flange 53, and the two flanges 50 are respectively assembled on the cylinder liner 20 At both ends of the axial direction, the two flanges 50 are respectively provided with air intake passages 54, and the two air intake passages 54 are respectively connected with the two limit passages 31, and the two flanges 50 are respectively provided with exhaust passages 51 , there is a phase difference between the intake channel 54 and the exhaust channel 51 on the same flange 50 . In this way, while the integrity of the bearing 200 is ensured, the reliability of suction and exhaust of the cylinder liner 20 is ensured.

As shown in FIG. 10 and FIG. 17 , the intake passage 54 includes a first intake passage segment 541 and a second intake passage segment 542 connected in sequence, the first intake passage segment 541 extends radially along the flange 50 , The second intake passage section 542 extends along the axial direction of the flange 50 . In this way, the communication reliability between the intake passage 54 and the variable volume cavity 311 is ensured.

As shown in Figure 17, an exhaust groove 55 is provided on the end surface of the flange 50 away from the cylinder liner 20, and the bottom of the exhaust groove 55 is provided with an exhaust communication port 551 and communicates with the limiting channel 31, and the exhaust communication The port 551 extends in the axial direction of the flange 50 . In this way, the exhaust reliability of the cylinder liner 20 is ensured.

As shown in Figure 17, the end of the air intake passage 54 is the intake communication port, and the initial end of the exhaust passage 51 is the exhaust communication port 551. When any slider 40 is in the intake position, the intake communication port is connected to the corresponding The variable volume chamber 311 is in conduction; when any slider 40 is in the exhaust position, the corresponding variable volume chamber 311 is in conduction with the exhaust communication port 551 .

Other usage occasions: the compressor can be used as an expander by exchanging the positions of the suction port and the exhaust port. That is, the exhaust port of the compressor is used as the suction port of the expander, and high-pressure gas is passed in, and other pushing mechanisms rotate, and the gas is discharged through the suction port of the compressor (exhaust port of the expander) after expansion.

When the fluid machine is an expander, the end of the intake passage 54 is the intake communication port, and the initial end of the exhaust passage 51 is the exhaust communication port 551. When any slider 40 is at the intake position, the exhaust communication port 551 is in communication with the corresponding variable volume cavity 311; when any slider 40 is in the exhaust position, the corresponding variable volume cavity 311 is in communication with the intake port.

As shown in Figure 22 to Figure 25, the projection of the slider 40 in its sliding direction is adapted to the section of the limiting channel 31, wherein Figure 22 shows the chamfering of the direction slider and the corresponding intersecting groove structure 30, Figure 23 It is a trapezoidal slider and the corresponding intersecting groove structure 30, FIG. 24 shows the chamfering of the trapezoidal slider and the corresponding intersecting groove structure 30, and FIG. 25 shows a semicircle+straight edge slider and the corresponding intersecting groove structure 30.

It should be noted that the terminology used here is only for describing specific implementations, and is not intended to limit the exemplary implementations according to the present application. As used herein, unless the context clearly dictates otherwise, the singular is intended to include the plural, and it should also be understood that when the terms "comprising" and/or "comprising" are used in this specification, they mean There are features, steps, operations, means, components and/or combinations thereof.

The relative arrangements of components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present invention unless specifically stated otherwise. At the same time, it should be understood that, for the convenience of description, the sizes of the various parts shown in the drawings are not drawn according to the actual proportional relationship. Techniques, methods and devices known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, such techniques, methods and devices should be considered part of the Authorized Specification. In all examples shown and discussed herein, any specific values should be construed as illustrative only, and not as limiting. Therefore, other examples of the exemplary embodiment may have different values. It should be noted that like numerals and letters denote like items in the following figures, therefore, once an item is defined in one figure, it does not require further discussion in subsequent figures.

For the convenience of description, spatially relative terms may be used here, such as "on ...", "over ...", "on the surface of ...", "above", etc., to describe The spatial positional relationship between one device or feature shown and other devices or features. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, devices described as "above" or "above" other devices or configurations would then be oriented "beneath" or "above" the other devices or configurations. under other devices or configurations”. Thus, the exemplary term "above" can encompass both an orientation of "above" and "beneath". The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptions used herein interpreted accordingly.

It should be noted that the terminology used here is only for describing specific implementations, and is not intended to limit the exemplary implementations according to the present application. As used herein, unless the context clearly dictates otherwise, the singular is intended to include the plural, and it should also be understood that when the terms "comprising" and/or "comprising" are used in this specification, they mean There are features, steps, operations, means, components and/or combinations thereof.

It should be noted that the terms "first" and "second" in the description and claims of the present application and the above drawings are used to distinguish similar objects, but not necessarily used to describe a specific sequence or sequence. It is to be understood that the data so used are interchangeable under appropriate circumstances such that the embodiments of the application described herein can be practiced in sequences other than those illustrated or described herein.

The above descriptions are only preferred embodiments of the present invention, and are not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and changes. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present invention shall be included within the protection scope of the present invention.

Claims (33)

1. A fluid machine having a bearing, comprising:

a crankshaft (10), the crankshaft (10) being provided with two eccentric portions (11) along its axial direction;

the crankshaft (10) and the cylinder sleeve (20) are eccentrically arranged, and the eccentric distance is fixed;

the bearing (200) is arranged in the cylinder sleeve (20), and the outer ring of the bearing (200) is attached to the inner wall of the cylinder sleeve (20);

The cross groove structure (30), the cross groove structure (30) is rotatably arranged in the cylinder sleeve (20), the outer peripheral surface of the cross groove structure (30) is attached to the inner ring of the bearing (200), the ratio between the height H1 of the bearing (200) and the height H2 of the cylinder sleeve (20) is more than 0.9 and less than 1, the cross groove structure (30) is provided with two limiting channels (31), the two limiting channels (31) are sequentially arranged along the axial direction of the crankshaft (10), and the extending direction of the limiting channels (31) is perpendicular to the axial direction of the crankshaft (10);

the sliding block (40), the sliding block (40) has through-hole (41), the sliding block (40) is two, two eccentric part (11) correspond to stretch into two in the through-hole (41) of sliding block (40), two sliding block (40) correspond the slip setting two in spacing passageway (31) and form variable volume chamber (311), variable volume chamber (311) are located the slip direction of sliding block (40), bent axle (10) rotate in order to drive sliding block (40) are in spacing passageway (31) reciprocating sliding is simultaneously with cross groove structure (30) interact, make cross groove structure (30) slider (40) are in cylinder liner (20) internal rotation.

2. The fluid machine according to claim 1, characterized in that between the height H1 of the bearing (200) and the height H2 of the cylinder liner (20) is: H2-H1 is more than or equal to 0.003mm and less than or equal to 0.1mm.

3. The fluid machine according to claim 1, characterized in that the two eccentric portions (11) have a phase difference of a first angle a, the eccentric amounts of the two eccentric portions (11) are equal, and the two limiting channels (31) have a phase difference of a second angle B in the extending direction, wherein the first angle a is twice the second angle B.

4. The fluid machine according to claim 1, characterized in that the eccentric amount of the eccentric portion (11) is equal to the fitting eccentric amount of the crankshaft (10) and the cylinder liner (20).

5. The fluid machine according to claim 1, wherein both ends of the limiting passage (31) penetrate to the outer peripheral surface of the intersecting groove structure (30).

6. The fluid machine according to claim 1, wherein two sliding blocks (40) are arranged concentrically with two eccentric portions (11), the sliding blocks (40) do circular motion around the eccentric portions (11), a first rotating gap is arranged between the hole wall of the through hole (41) and the eccentric portions (11), and the first rotating gap ranges from 0.005mm to 0.05mm.

7. The fluid machine according to claim 1, wherein the cylinder liner (20) has a circumferential collar (28) at its outer periphery, and a plurality of spaced apart elongated holes (281) are provided in the circumferential collar (28).

8. A fluid machine according to claim 3, wherein the first included angle a is 160-200 degrees; the second included angle B is 80-100 degrees.

9. The fluid machine according to claim 1, further comprising a flange (50), said flange (50) being arranged at an axial end of said cylinder liner (20), said crankshaft (10) being arranged concentrically with said flange (50).

10. The fluid machine according to claim 9, characterized in that there is a first assembly gap between the crankshaft (10) and the flange (50), the first assembly gap being in the range of 0.005mm to 0.05mm.

11. The fluid machine of claim 10, wherein the first assembly gap is in the range of 0.01 to 0.03mm.

12. The fluid machine according to claim 1, wherein the eccentric portion (11) has an arc surface, and a central angle of the arc surface is 180 degrees or more.

13. A fluid machine according to claim 1, characterized in that the eccentric (11) is cylindrical.

14. The fluid machine of claim 13, wherein the fluid machine is further configured to,

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 alternatively, the first and second heat exchangers may be,

The proximal end of the eccentric part (11) protrudes out of the outer circle of the shaft body part (12) of the crankshaft (10); or alternatively, the first and second heat exchangers may be,

the proximal end of the eccentric portion (11) is located inside the outer circumference of the shaft body portion (12) of the crankshaft (10).

15. The fluid machine according to claim 1, wherein the slider (40) comprises a plurality of substructures, and wherein the plurality of substructures are spliced to define the through hole (41).

16. Fluid machine according to claim 1, characterized in that two of the eccentric parts (11) are arranged at intervals in the axial direction of the crankshaft (10).

17. The fluid machine according to claim 1, characterized in that the cross-slot structure (30) has a central bore (32), through which central bore (32) two of the limiting channels (31) communicate, the bore diameter of the central bore (32) being larger than the diameter of the shaft body part (12) of the crankshaft (10).

18. The fluid machine according to claim 17, characterized in that the bore diameter of the central bore (32) is larger than the diameter of the eccentric section (11).

19. Fluid machine according to claim 1, characterized in that the projection of the slider (40) in the axial direction of the through hole (41) has two relatively parallel straight segments and an arc segment connecting the ends of the two straight segments.

20. The fluid machine according to claim 1, characterized in that the slide (40) has a pressing surface (42) facing the end of the limiting channel (31), the pressing surface (42) acting as a head of the slide (40), the pressing surface (42) facing the variable volume chamber (311).

21. The fluid machine according to claim 20, wherein the pressing surface (42) is an arc surface, and a distance between an arc center of the arc surface and a center of the through hole (41) is equal to an eccentric amount of the eccentric portion (11).

22. The fluid machine of claim 21, wherein the fluid machine is further configured to,

the radius of curvature of the cambered surface is equal to the radius of the inner circle of the cylinder sleeve (20); or alternatively, the first and second heat exchangers may be,

the radius of curvature of the cambered surface and the radius of the inner circle of the cylinder sleeve (20) have a difference value, and the range of the difference value is-0.05 mm-0.025 mm.

23. The fluid machine of claim 22, wherein the difference is in the range of-0.02 to 0.02mm.

24. The fluid machine according to claim 20, characterized in that the projected area S of the pressing surface (42) in the sliding direction of the slider (40) _{Sliding block} The area of the compression exhaust port with the cylinder sleeve (20) is S _{Row of rows} The following are satisfied: s is S _{Sliding block} /S _{Row of rows} The value of (2) is 8 to 25.

25. The fluid machine of claim 24, wherein S _{Sliding block} /S _{Row of rows} The value of (2) is 12 to 18.

26. The fluid machine according to claim 1, characterized in that the fluid machine comprises two flanges (50), the two flanges (50) are respectively assembled at two axial ends of the cylinder sleeve (20), the two flanges (50) are respectively provided with an air inlet channel (54), the two air inlet channels (54) are respectively communicated with the two limiting channels (31), the two flanges (50) are respectively provided with an air outlet channel (51), and a phase difference exists between the air inlet channels (54) and the air outlet channels (51) on the same flange (50).

27. The fluid machine of claim 26, wherein the intake passage (54) includes a first intake passage section (541) and a second intake passage section (542) that are in sequential communication, the first intake passage section (541) extending in a radial direction of the flange (50), the second intake passage section (542) extending in an axial direction of the flange (50).

28. The fluid machine according to claim 26, characterized in that an exhaust groove (55) is provided on a side end surface of the flange (50) facing away from the cylinder liner (20), an exhaust communication port (551) is provided at a groove bottom of the exhaust groove (55) and communicates with the limiting passage (31), and the exhaust communication port (551) extends in an axial direction of the flange (50).

29. The fluid machine according to claim 26, wherein the air intake passage (54) is terminated with an air intake communication port, the initial end of the air exhaust passage (51) is an air exhaust communication port (551),

when any sliding block (40) is positioned at an air inlet position, the air inlet communication port is communicated with the corresponding variable-volume cavity (311);

when any one of the sliding blocks (40) is at the exhaust position, the corresponding variable-volume cavity (311) is communicated with the exhaust communication port (551).

30. The fluid machine of claim 29, wherein the fluid machine is a compressor.

31. The fluid machine according to claim 26, wherein the air intake passage (54) is terminated with an air intake communication port, the initial end of the air exhaust passage (51) is an air exhaust communication port (551),

when any one of the sliding blocks (40) is at an air inlet position, the air exhaust communication port (551) is communicated with the corresponding variable-volume cavity (311);

when any sliding block (40) is at the exhaust position, the corresponding variable-volume cavity (311) is communicated with the air inlet communication port.

32. The fluid machine of claim 31, wherein the fluid machine is an expander.

33. A heat exchange device comprising a fluid machine, characterized in that the fluid machine is a fluid machine according to any one of claims 1 to 32.

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