CN116241468A - Fluid machine and heat exchange device with bearing - Google Patents

Abstract

The invention provides a fluid machine with a bearing and heat exchange equipment, wherein the fluid machine with the bearing comprises a crankshaft, a cylinder sleeve, a bearing, a cross groove structure and a sliding block, and the crankshaft is provided with two eccentric parts; the crankshaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; at least one bearing is arranged at the axial end face of the cylinder sleeve and positioned at the outer side of the cylinder sleeve; the crossed groove structure is rotatably arranged in the cylinder sleeve, part of the outer circumferential surface of the axial direction of the crossed groove structure is attached to the inner ring of the bearing, two limiting channels of the crossed groove structure are sequentially arranged along the axial direction of the crankshaft, and the extending direction of the limiting channels is perpendicular to the axial direction of the crankshaft; the sliding blocks are provided with through holes, the two eccentric parts correspondingly extend into the two through holes of the two sliding blocks, and the two sliding blocks are correspondingly arranged in the two limiting channels in a sliding manner and form a variable-volume cavity. The invention solves the problems of lower energy efficiency and larger 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 arranged eccentrically and the eccentric distance is fixed; there is at least one bearing, and the bearing is arranged on the axial end surface of the cylinder liner and is located outside the cylinder liner; the cross groove structure is rotatably arranged in the cylinder liner, and the cross groove The axial part of the outer peripheral surface of the structure fits with the inner ring of the bearing. The cross groove structure has two limiting channels. The two limiting channels are arranged in sequence along the axial direction of the crankshaft. The extending direction of the limiting channels is perpendicular to the crankshaft. Axial; the slider has two through holes, 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 limiting channels and form variable The volume cavity and the variable volume cavity are located in the sliding direction of the slider. The crankshaft rotates to drive the slider to slide back and forth in the limiting channel while interacting with the intersecting groove structure, so that the intersecting groove structure and the slider rotate in the cylinder liner.

Further, only one end of the axial end of the cylinder liner is provided with a bearing; or, both ends of the axial end of the cylinder liner are provided with bearings.

Further, the diameter D1 of the inner ring of the bearing and the diameter D3 of the outer peripheral surface of the cylinder liner meet: D1-D3 is 0.003-0.02mm.

Further, the diameter D2 of the outer peripheral surface of the intersecting groove structure and the diameter D3 of the inner wall surface of the cylinder liner satisfy: D2-D3 is 0.02-0.05 mm.

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 intersecting groove structure is arranged coaxially with the cylinder liner, and there is a second rotation gap between the outer peripheral surface of the intersecting groove structure and the inner wall surface of the cylinder liner, and the second rotation gap ranges from 0.005 mm to 0.05 mm.

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, the crankshaft is concentrically arranged with the flange, and the flange is eccentrically arranged with the cylinder liner.

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 0.01-0.03mm.

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.

Furthermore, when only one end of the axial end of the cylinder liner is provided with a bearing, the fluid machine includes two flanges, and the two flanges are respectively assembled on the axial end of the cylinder liner and the axial end of the bearing. The sleeve is provided with a radial suction hole and an axial distribution hole connected with the radial suction hole; wherein, the radial suction hole communicates with the corresponding limiting channel in the radial direction of the cylinder liner, and the bearing is provided with a channel for connecting with the axial distribution hole. Connected suction through holes, the flange on the bearing side has a suction channel, one end of the suction channel communicates with the suction through hole, and the other end of the suction channel communicates with the corresponding limit channel at the bearing.

Further, the inner wall surface of the cylinder liner has an air suction cavity, and the air suction cavity communicates with the radial air suction holes.

Further, the suction cavity extends a first preset distance around the inner wall surface of the cylinder liner to form an arc-shaped suction cavity.

Further, the cylinder liner has a compression exhaust port, and there is a phase difference between the compression exhaust port and the radial suction hole, an exhaust chamber is opened on the outer wall of the cylinder liner, and the compression exhaust port is connected to the inner wall of the cylinder liner. At the exhaust cavity, the fluid machine also includes an exhaust valve assembly, which is arranged in the exhaust cavity and corresponding to the compression exhaust port.

Further, the flange on the bearing side is provided with a flange exhaust port, the flange exhaust port communicates with the limiting passage at the bearing, and the flange exhaust port is located inside the inner ring side of the bearing.

Further, the end of the radial air suction hole is the first air intake communication port, and the end of the air suction channel is the second air intake communication port. When the slider at the cylinder liner is at the intake position, the first air intake communication port It is connected with the corresponding variable volume cavity. When the slider at the cylinder liner is at the exhaust position, the corresponding variable volume cavity is connected with the compression exhaust port; when the slider at the bearing is at the intake position, the second inlet The gas communication port is connected to the corresponding variable volume cavity, and when the slider at the bearing is in the exhaust position, the corresponding variable volume cavity is connected to the flange exhaust port.

Further, the fluid machine is a compressor.

Further, the end of the radial air suction hole is the first air intake communication port, and the end of the air suction channel is the second air intake communication port. When the slider at the cylinder liner is at the intake position, the compression exhaust port and the corresponding When the slider at the cylinder liner is at the exhaust position, the corresponding variable volume cavity is connected with the first air intake port; when the slider at the bearing is at the intake position, the flange row The air port is in communication with the corresponding variable volume chamber, and when the slider at the bearing is in the exhaust position, the corresponding variable volume chamber is in communication with the second air intake port.

Further, the fluid machine is an expander.

Further, when both ends of the axial end of the cylinder liner are provided with bearings, the cylinder liner is provided with a radial suction hole and an axial split hole communicating with the radial suction hole; wherein, the axial split hole One end communicates with one of the two limiting passages, and the other end of the axial distribution hole communicates with the other of the two limiting passages.

Further, the inner wall of the cylinder liner has an air suction cavity, which communicates with the axial distribution hole.

Further, the suction cavity extends a first preset distance around the inner wall surface of the cylinder liner to form an arc-shaped suction cavity.

Further, there are two suction cavities, and the two suction cavities are arranged at intervals along the axial direction of the cylinder liner, and the two suction cavities correspond to and communicate with the two limiting passages one by one.

Further, the cylinder liner has a compression exhaust port, and there is a phase difference between the compression exhaust port and the radial suction hole.

Further, there are two compression and exhaust ports, and the two compression and exhaust ports are arranged at intervals along the axial direction of the cylinder liner, and the two compression and exhaust ports correspond to and communicate with the two limiting passages one by one.

Further, the end of the suction chamber is an air intake communication port. When any slider is in the intake position, the intake communication port is connected to the corresponding variable volume chamber; when any slider is in the exhaust position, the corresponding The variable volume cavity is connected with the compression exhaust port.

Further, the fluid machine is a compressor.

Further, the end of the suction chamber is an air intake communication port. When any slider is in the intake position, the compression exhaust port is connected to the corresponding variable volume chamber; when any slider is in the exhaust position, the corresponding The variable volume cavity of the air inlet is communicated with 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 at the axial end surface of the cylinder liner and on the outside of the cylinder liner, the axial part of the outer peripheral surface of the intersecting groove structure is attached to the inner ring of the bearing, so that the outer peripheral surface of the intersecting groove structure passes through The bearing support reduces friction, so that the sliding friction between the circumferential outer surface of the intersecting groove structure and the inner wall of the cylinder liner changes into the rolling friction between the circumferential outer surface of the intersecting groove structure and the bearing, which reduces the mechanical friction power consumption. Among them, the bearing The inner ring of the bearing is matched with the cross groove structure, and the inner ring of the bearing is matched 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 the compressor according to Embodiment 1 of the present invention;

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

Fig. 5 shows the schematic cross-sectional structural diagram of the J-J angle of view in Fig. 4;

Fig. 6 shows the schematic diagram of the cross-sectional structure of the T-T perspective in Fig. 4;

Fig. 7 shows a schematic cross-sectional structural view of the K-K perspective in Fig. 4;

Figure 8 shows a schematic diagram of the exploded structure of the pump body assembly in Figure 3;

Fig. 9 shows the crankshaft in Fig. 8, the cross groove structure, the assembling structure schematic diagram of slide block;

Fig. 10 shows the schematic cross-sectional structure diagram of the crankshaft, the intersecting groove structure and the slide block in Fig. 9;

Fig. 11 shows a schematic structural view of the shaft body part of the crankshaft and the eccentricity of the two eccentric parts in Fig. 9;

Fig. 12 shows a structural schematic diagram of the assembly eccentricity of the crankshaft and cylinder liner in Fig. 8;

Figure 13 shows a schematic structural view of the slider in Figure 8 in the axial direction of the through hole;

Figure 14 shows a schematic structural view of the cylinder liner in Figure 8;

Fig. 15 shows a structural schematic diagram of another viewing angle of the cylinder liner in Fig. 14;

Fig. 16 shows a schematic cross-sectional structural view of the W-W perspective in Fig. 15;

Fig. 17 shows a schematic structural diagram of the S-S perspective in Fig. 16;

Fig. 18 shows a schematic diagram of the internal structure of a compressor according to Embodiment 2 of the present invention;

Fig. 19 shows a schematic cross-sectional structural view of the pump body assembly in Fig. 18;

Fig. 20 shows a schematic diagram of the internal structure of a compressor according to Embodiment 3 of the present invention;

Fig. 21 shows a schematic cross-sectional structural view of the pump body assembly in Fig. 20;

Fig. 22 shows a schematic diagram of the mechanism principle of compressor operation in the prior art;

Figure 23 shows a schematic diagram of the mechanism principle of the improved compressor operation in the prior art;

Fig. 24 shows a schematic diagram of the operating mechanism of the compressor in Fig. 23. In this figure, the force arm of the drive shaft driving the slider to rotate is shown;

Fig. 25 shows a schematic diagram of the operating mechanism of the compressor in Fig. 23, in which 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; 22, compression exhaust port; 23, suction cavity; 25, exhaust cavity; 220, radial suction hole; 230, axial distribution 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; 52, upper flange; 53, lower flange; 56, suction channel; 57, flange exhaust port; 58, cover plate;

60. Exhaust valve assembly;

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; 201, suction through hole.

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 22, 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 23, 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 24, 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 to the slider The angle between the sliding directions in the limit slot.

As shown in Figure 25, 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, 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 eccentrically arranged and the eccentric distance is fixed; there is at least one bearing 200, and the bearing 200 is arranged on the axial end surface of the cylinder liner 20 and is located outside the cylinder liner 20; the cross groove structure 30 is rotatably arranged in the cylinder liner 20, and The axial part of the outer peripheral surface of the intersecting groove structure 30 is attached to the inner ring of the bearing 200. The intersecting groove structure 30 has two limiting passages 31, and the two limiting passages 31 are sequentially arranged along the axial direction of the crankshaft 10. The extending direction of the 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 two through holes 41 of the two sliders 40 correspondingly. Two sliders 40 are correspondingly slidably arranged in the two limiting passages 31 and form variable volume chambers 311. The variable volume chambers 311 are located in the sliding direction of the sliders 40, and the crankshaft 10 rotates to drive the sliders 40 to reciprocate in the limiting passages 31. While sliding, it interacts with the intersecting groove structure 30 , so that the intersecting groove structure 30 and the slider 40 rotate in the cylinder sleeve 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 at the axial end surface of the cylinder liner 20 and outside the cylinder liner 20, the axial part of the outer peripheral surface of the intersecting groove structure 30 is attached to the inner ring of the bearing 200, so that the intersecting groove The outer peripheral surface of the structure 30 is supported by the bearing 200 to reduce friction, so that the sliding friction between the outer peripheral surface of the intersecting groove structure 30 and the inner wall of the cylinder liner 20 becomes the rolling friction between the outer peripheral surface of the intersecting groove structure 30 and the bearing 200 , reducing 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.

Three optional implementations will be given below to introduce the structure of the fluid machine in detail, so as to better explain the operation method of the fluid machine through structural features.

Embodiment one

As shown in FIGS. 3 to 17 , in this embodiment, only one axial end of the cylinder liner 20 is provided with a bearing 200 , and the bearing 200 is located above the one axial end of the cylinder liner 20 .

Optionally, the diameter D1 of the inner ring of the bearing 200 and the diameter D3 of the outer peripheral surface of the cylinder liner 20 satisfy: D1-D3 is 0.003-0.02 mm.

Optionally, the diameter D2 of the outer peripheral surface of the intersecting groove structure 30 and the diameter D3 of the inner wall surface of the cylinder liner 20 satisfy: D2-D3 is 0.02-0.05 mm.

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 Fig. 3 to Fig. 17, 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 center 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 adjusting the center 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. 11, the eccentricity of the two eccentric parts 11 is equal to e, and as shown in FIG. 20 is 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 FIG. 8 , 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 .

As shown in FIGS. 8 to 11 , the shaft part 12 of the crankshaft 10 is integrally formed, and the shaft part 12 has only one axis. 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 FIGS. 8 to 11 , the shaft portion 12 of the crankshaft 10 is integrally formed with the eccentric portion 11 . 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.

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.

Optionally, the intersecting groove structure 30 is arranged coaxially with the cylinder liner 20, and there is a second rotation gap between the outer peripheral surface of the intersecting groove structure 30 and the inner wall surface of the cylinder liner 20, and the range of the second rotation gap is 0.005 mm to 0.05 mm .

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.

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 0.01-0.03 mm.

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 FIGS. 8 to 11 , 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 of the crankshaft 10 .

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

Optionally, the proximal end of the eccentric portion 11 is located inside the outer circle of the shaft portion 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 FIGS. 8 to 11 , 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. 8 , 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 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 Figure 12, the structural diagram of the assembly eccentricity of the crankshaft 10 and the cylinder liner 20, the symbol U in the figure represents the center of the eccentric part 11 of the crankshaft 10, the symbol P represents the center of the cylinder liner 20, and the symbol Z represents the center of the crankshaft 10 The center of the shaft part 12.

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.

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 range of the difference is -0.05mm˜0.025mm.

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

Optionally, the projected area S of the extrusion surface 42 in the sliding direction of the slider 40 satisfies between the area S of the _slider and the compression exhaust port 22 of the cylinder liner 20 as S _rows : the value of the S _slider /S _row 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 Figure 5, Figure 7, Figure 14 to Figure 17, the fluid machine includes two flanges 50, and the two flanges 50 are respectively assembled on the axial end of the cylinder liner 20 and the axial end of the bearing 200, the cylinder The sleeve 20 is provided with a radial suction hole 220 and an axial distribution hole 230 communicating with the radial suction hole 220; wherein, the radial suction hole 220 communicates with the radially corresponding limiting channel 31 of the cylinder liner 20, and the bearing 200 A suction through-hole 201 for communicating with the axial split hole 230 is provided, and the flange 50 on the side of the bearing 200 has a suction channel 56, and one end of the suction channel 56 communicates with the suction through-hole 201, and the side of the suction channel 56 The other end communicates with the corresponding limiting channel 31 at the bearing 200 . In this way, the suction reliability of the compressor is ensured.

It should be noted that, in the present embodiment, the flange 50 also includes a cover plate 58, and the cover plate 58 covers the processing opening of the suction channel 56 away from the cylinder liner 20, so as to seal the suction channel 56, It is ensured that gas can smoothly enter the limiting passage 31 at the bearing 200 from the suction through hole 201 through the suction passage 56 .

As shown in FIGS. 1 to 17 , the inner wall surface of the cylinder liner 20 has an air suction chamber 23 , and the air suction chamber 23 communicates with the radial air suction holes 220 . In this way, it is ensured that the suction chamber 23 can store a large amount of gas, so that the variable volume chamber 311 can be fully suctioned, so that the compressor can take in enough air, and when the suction is insufficient, the stored gas can be supplied in time Give the variable volume chamber 311 to ensure the compression efficiency of the compressor.

Optionally, the suction cavity 23 is a cavity formed by radially hollowing out the inner wall of the cylinder liner 20, and there may be one suction cavity 23, or two upper and lower ones.

Specifically, the suction cavity 23 extends a first preset distance around the inner wall surface of the cylinder liner 20 to form an arc-shaped suction cavity 23 . In this way, it is ensured that the volume of the suction chamber 23 is large enough to store a large amount of gas.

As shown in Figure 6, Figures 15 and 17, the cylinder liner 20 has a compression exhaust port 22, and there is a phase difference between the compression exhaust port 22 and the radial suction hole 220, and the outer wall of the cylinder liner 20 is provided with an exhaust cavity 25, the compression exhaust port 22 is connected to the exhaust cavity 25 by the inner wall of the cylinder liner 20, and the fluid machine also includes an exhaust valve assembly 60, which is arranged in the exhaust cavity 25 and corresponds to the compression exhaust port 22 settings.

Optionally, exhaust valve assembly 60 is mounted to cylinder liner 20 by fasteners.

As shown in Figure 7, the flange 50 on the side of the bearing 200 is provided with a flange exhaust port 57, the flange exhaust port 57 communicates with the limiting channel 31 located at the bearing 200, and the flange exhaust port 57 is located at the bearing 200 within the inner ring side of the In this way, the bearing 200 is prevented from covering the flange discharge port 57, thereby ensuring the reliability of the discharge of the compressor.

It should be noted that, in the embodiment, the end of the radial air suction hole 220 is the first air intake communication port, and the end of the air suction passage 56 is the second air intake communication port. When the slider 40 at the cylinder liner 20 is in the At the intake position, the first air intake port communicates with the corresponding variable volume chamber 311, and when the slider 40 at the cylinder liner 20 is at the exhaust position, the corresponding variable volume chamber 311 communicates with the compression exhaust port 22 ; When the slider 40 at the bearing 200 is at the air intake position, the second air intake communication port is connected to the corresponding variable volume cavity 311, and when the slider 40 at the bearing 200 is at the exhaust position, the corresponding variable volume cavity 311 is in communication with the flange exhaust port 57.

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

As shown in Figure 3, the motor assembly 82 drives the crankshaft 10 to rotate, and the two eccentric parts 11 of the crankshaft 10 respectively drive the corresponding two sliders 40 to move. When the slider 40 revolves around the axis of the crankshaft 10, the slider 40 Relative to the eccentric part 11, the slider 40 reciprocates along the limiting channel 31, and drives the cross groove structure 30 to rotate in the cylinder liner 20. The slider 40 reciprocates along the limiting channel 31 while revolving to form a cross slide Movement mode of the block mechanism.

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 radial air suction hole 220 is the first air intake communication port, and the end of the air suction passage 56 is the second air intake communication port. When the slider 40 at the cylinder liner 20 is in the air intake position, the compression exhaust port 22 is in communication with the corresponding variable volume chamber 311, and when the slider 40 at the cylinder liner 20 is in the exhaust position, the corresponding variable volume chamber 311 is in communication with the first intake port; When the slider 40 at the bearing 200 is at the intake position, the flange exhaust port 57 is in communication with the corresponding variable volume cavity 311, and when the slider 40 at the bearing 200 is at the exhaust position, the corresponding variable volume cavity 311 is connected to the exhaust position. The second air intake communication port is conducted.

Embodiment two

As shown in FIGS. 18 and 19 , a bearing 200 is provided at one end of the axial end portion of the cylinder liner 20 . The difference between this embodiment and Embodiment 1 is that the bearing 200 of this embodiment is located below the axial end of the cylinder liner 20 .

It should be noted that the relative positions of the cylinder liner 20 and the bearing 200 in this embodiment are only different from the upper and lower positions, and the suction and exhaust method of the first embodiment is also applicable to the second embodiment.

Embodiment Three

As shown in Figure 20 and Figure 21, when both ends of the axial end of the cylinder liner 20 are provided with bearings 200, the cylinder liner 20 is provided with a radial suction hole 220 and communicates with the radial suction hole 220 The axial distribution hole 230; wherein, one end of the axial distribution hole 230 communicates with one of the two limiting passages 31, and the other end of the axial distribution hole 230 communicates with the other of the two limiting passages 31.

As shown in FIG. 21 , the inner wall of the cylinder liner 20 has an air suction chamber 23 , and the air suction chamber 23 communicates with the axial distribution hole 230 .

Optionally, the suction cavity 23 extends a first preset distance around the inner wall surface of the cylinder liner 20 to form an arc-shaped suction cavity 23 .

As shown in FIG. 21 , there are two suction chambers 23 , and the two suction chambers 23 are arranged at intervals along the axial direction of the cylinder liner 20 . The two suction chambers 23 correspond to and communicate with the two limiting passages 31 one by one.

It should be noted that, in this embodiment, the cylinder liner 20 has a compression exhaust port 22, and there is a phase difference between the compression exhaust port 22 and the radial suction hole 220 (the compression exhaust port on the cylinder liner 20 of this embodiment The air port 22 is consistent with the position and opening method of the compression exhaust port 22 in Fig. 17 in Embodiment 1, and will not be repeated here).

Optionally, there are two compression exhaust ports 22, and the two compression exhaust ports 22 are arranged at intervals along the axial direction of the cylinder liner 20. The two compression exhaust ports 22 correspond to the two two limiting passages 31 one by one and connected.

It should be noted that, when the fluid machine is a compressor, the end of the suction chamber 23 is an air intake communication port, and when any slider 40 is in the intake position, the intake communication port is in communication with the corresponding variable volume chamber 311 ; When any slider 40 is in the exhaust position, the corresponding variable volume cavity 311 is in communication with the compression exhaust port 22 .

It should be noted that, when the fluid machine is an expander, the end of the suction chamber 23 is an intake communication port, and when any slider 40 is at the intake position, the compression exhaust port 22 is connected to the corresponding variable volume chamber 311. When any slider 40 is in the exhaust position, the corresponding variable volume cavity 311 is in communication with the intake port.

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 (47)

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;

-a bearing (200), at least one bearing (200), the bearing (200) being arranged at an axial end face of the cylinder liner (20) and being located outside the cylinder liner (20);

the cross groove structure (30), the cross groove structure (30) is rotatably arranged in the cylinder sleeve (20), part of the outer circumferential surface of the axial direction of the cross groove structure (30) is attached to the inner ring of the bearing (200), 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. A fluid machine as claimed in claim 1, wherein,

-only one end of the axial end of the cylinder liner (20) is provided with the bearing (200); or alternatively, the first and second heat exchangers may be,

the bearings (200) are arranged at both ends of the axial end part of the cylinder sleeve (20).

3. The fluid machine according to claim 1, characterized in that the diameter D1 of the inner ring of the bearing (200) and the diameter D3 of the outer circumferential surface of the cylinder liner (20) satisfy: D1-D3 is 0.003-0.02mm.

4. The fluid machine according to claim 1, wherein a diameter D2 of the outer peripheral surface of the intersecting groove structure (30) and a diameter D3 of the inner wall surface of the cylinder liner (20) satisfy: D2-D3 is 0.02-0.05mm.

5. 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.

6. 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).

7. 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).

8. 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.

9. The fluid machine according to claim 1, wherein the cross groove structure (30) is coaxially arranged with the cylinder liner (20), and a second rotational gap is provided between an outer circumferential surface of the cross groove structure (30) and an inner wall surface of the cylinder liner (20), and the second rotational gap ranges from 0.005mm to 0.05mm.

10. The fluid machine of claim 5, wherein the first included angle a is 160 degrees to 200 degrees; the second included angle B is 80-100 degrees.

11. 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), said flange (50) being arranged eccentrically with respect to said cylinder liner (20).

12. The fluid machine according to claim 11, characterized in that 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.

13. The fluid machine of claim 12, wherein the first assembly gap is in the range of 0.01 to 0.03mm.

14. 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.

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

16. The fluid machine of claim 15, 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 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 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 of the crankshaft (10).

17. 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).

18. 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).

19. The fluid machine according to claim 1, characterized in that the cross-slot structure (30) has a central hole (32), through which central hole (32) two limit channels (31) communicate, the central hole (32) having a larger bore diameter than the shaft portion of the crankshaft (10).

20. The fluid machine according to claim 19, characterized in that the bore diameter of the central bore (32) is larger than the diameter of the eccentric portion (11).

21. 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.

22. 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).

23. The fluid machine according to claim 22, 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).

24. The fluid machine of claim 23, 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.

25. The fluid machine of claim 24, wherein the difference is in the range of-0.02 to 0.02mm.

26. The fluid machine according to claim 22, 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 (22) 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.

27. The fluid machine of claim 26, wherein S _{Sliding block} /S _{Row of rows} The value of (2) is 12 to 18.

28. A fluid machine as claimed in claim 2, wherein,

when only one end of the axial end portion of the cylinder sleeve (20) is provided with the bearing (200), the fluid machine comprises two flanges (50), the two flanges (50) are respectively assembled at the axial end portion of the cylinder sleeve (20) and the axial end portion of the bearing (200), and the cylinder sleeve (20) is provided with a radial air suction hole (220) and an axial flow dividing hole (230) communicated with the radial air suction hole (220);

The radial suction hole (220) is communicated with the limit channel (31) corresponding to the cylinder sleeve (20) in the radial direction, the bearing (200) is provided with a suction through hole (201) communicated with the axial flow dividing hole (230), the flange (50) positioned on the side of the bearing (200) is provided with a suction channel (56), one end of the suction channel (56) is communicated with the suction through hole (201), and the other end of the suction channel (56) is communicated with the limit channel (31) corresponding to the position of the bearing (200).

29. The fluid machine according to claim 28, wherein the inner wall surface of the cylinder liner (20) has a suction chamber (23), the suction chamber (23) being in communication with the radial suction holes (220).

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

31. The fluid machine of claim 28, wherein the cylinder liner (20) has a compression exhaust port (22), and a phase difference exists between the compression exhaust port (22) and the radial suction hole (220), an exhaust cavity (25) is formed in an outer wall of the cylinder liner (20), the compression exhaust port (22) is communicated to the exhaust cavity (25) by an inner wall of the cylinder liner (20), the fluid machine further comprises an exhaust valve assembly (60), and the exhaust valve assembly (60) is disposed in the exhaust cavity (25) and corresponds to the compression exhaust port (22).

32. The fluid machine according to claim 31, characterized in that the flange (50) at the side of the bearing (200) is provided with a flange exhaust port (57), the flange exhaust port (57) being in communication with the limiting channel (31) at the bearing (200), the flange exhaust port (57) being located inside the inner ring side of the bearing (200).

33. The fluid machine of claim 32, wherein the radial suction holes (220) terminate in a first suction communication port (2201), the suction channels (56) terminate in a second suction communication port (561),

when the sliding block (40) at the cylinder sleeve (20) is at an air inlet position, the first air inlet communication port (2201) is communicated with the corresponding variable-volume cavity (311), and when the sliding block (40) at the cylinder sleeve (20) is at an air outlet position, the corresponding variable-volume cavity (311) is communicated with the compression air outlet (22);

when the sliding block (40) at the bearing (200) is at an air inlet position, the second air inlet communication port (561) is communicated with the corresponding variable-volume cavity (311), and when the sliding block (40) at the bearing (200) is at an air outlet position, the corresponding variable-volume cavity (311) is communicated with the flange air outlet (57).

34. The fluid machine of claim 33, wherein the fluid machine is a compressor.

35. The fluid machine of claim 32, wherein the radial suction holes (220) terminate in a first inlet communication port, the suction channels (56) terminate in a second inlet communication port,

when the sliding block (40) at the cylinder sleeve (20) is at an air inlet position, the compression exhaust port (22) is communicated with the corresponding variable-volume cavity (311), and when the sliding block (40) at the cylinder sleeve (20) is at an air outlet position, the corresponding variable-volume cavity (311) is communicated with the first air inlet communication port;

when the sliding block (40) at the bearing (200) is at an air inlet position, the flange air outlet (57) is communicated with the corresponding variable-volume cavity (311), and when the sliding block (40) at the bearing (200) is at an air outlet position, the corresponding variable-volume cavity (311) is communicated with the second air inlet communication port.

36. The fluid machine of claim 35, wherein the fluid machine is an expander.

37. A fluid machine as claimed in claim 2, wherein,

when the bearings (200) are arranged at the two ends of the axial end part of the cylinder sleeve (20), the cylinder sleeve (20) is provided with radial air suction holes (220) and axial diversion holes (230) communicated with the radial air suction holes (220);

Wherein one end of the axial flow dividing hole (230) is communicated with one of the two limiting channels (31), and the other end of the axial flow dividing hole (230) is communicated with the other of the two limiting channels (31).

38. The fluid machine according to claim 37, wherein the inner wall surface of the cylinder liner (20) has a suction chamber (23), the suction chamber (23) being in communication with the axial flow diversion hole (230).

39. The fluid machine according to claim 38, wherein the suction chamber (23) extends a first predetermined distance around the circumference of the inner wall surface of the cylinder liner (20) to form an arc-shaped suction chamber (23).

40. The fluid machine according to claim 38, wherein the number of the air suction cavities (23) is two, the two air suction cavities (23) are arranged at intervals along the axial direction of the cylinder sleeve (20), and the two air suction cavities (23) are in one-to-one correspondence and are communicated with the two limit channels (31).

41. The fluid machine of claim 38, wherein the cylinder liner (20) has a compression exhaust port (22) and the radial suction hole (220) have a phase difference therebetween.

42. The fluid machine according to claim 41, wherein the number of the compression exhaust ports (22) is two, the two compression exhaust ports (22) are arranged at intervals along the axial direction of the cylinder sleeve (20), and the two compression exhaust ports (22) are in one-to-one correspondence and are communicated with the two limiting channels (31).

43. The fluid machine according to claim 42, wherein the suction chamber (23) terminates in an inlet communication port,

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 compression exhaust port (22).

44. The fluid machine of claim 43, wherein the fluid machine is a compressor.

45. The fluid machine according to claim 42, wherein the suction chamber (23) terminates in an inlet communication port,

when any sliding block (40) is at an air inlet position, the compression air outlet (22) 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.

46. The fluid machine of claim 45, wherein the fluid machine is an expander.

47. A heat exchange device comprising a fluid machine, characterized in that the fluid machine is a fluid machine as claimed in any one of claims 1 to 46.

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