WO2023226413A1 - Fluid machine and heat exchange device - Google Patents

Abstract

A fluid machine and a heat exchange device. The fluid machine comprises a crankshaft (10), a cylinder sleeve (20), a cross groove structure (30), sliding blocks (40), and two flanges (50). The crankshaft (10) is provided with two eccentric portions (11); the crankshaft (10) and the cylinder sleeve (20) are eccentrically provided and an eccentric distance is fixed; the cross groove structure (30) is rotatably provided in the cylinder sleeve (20); two limiting channels (31) of the cross groove structure (30) are sequentially provided in an axial direction of the crankshaft (10), and an extending direction of each limiting channel (31) is perpendicular to the axial direction of the crankshaft (10); the two eccentric portions (11) correspondingly extend into two through holes (41) of two sliding blocks (40), and the two sliding blocks (40) are correspondingly slidably provided in the two limiting channels (31) and variable volume cavities are formed. The two flanges (50) are respectively provided at two axial ends of the cylinder sleeve (20), one of the two flanges (50) is provided with an air inlet channel (54), the cylinder sleeve (20) is provided with a radial air suction hole (21), and the air inlet channel (54) and the radial air suction hole (21) are respectively communicated with two variable volume cavities. Therefore, air suction reliability of the fluid machine is ensured, and air suction loss caused by insufficient air suction of the fluid machine is avoided.

Description

Fluid machinery and heat exchange equipment

Related applications

This application claims priority to the Chinese patent application filed on May 23, 2022, with application number 202210565528.8 and titled "Fluid Machinery and Heat Exchange Equipment", the full text of which is hereby incorporated by reference.

Technical field

The present application relates to the technical field of heat exchange systems, specifically, to a fluid machine and heat exchange equipment.

Background technique

Fluid machinery in related technologies includes compressors, expanders, etc. Take a compressor as an example.

In accordance with national energy conservation and environmental protection policies and consumer 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, rolling rotor compressors have become relatively mature after nearly a hundred years of development. However, they are limited by structural principles and have limited room for optimization.

Contents of the invention

The main purpose of the present invention is to provide a fluid machine and heat exchange equipment. According to one aspect of the present application, a fluid machine is provided, including a crankshaft, a cylinder liner, a cross groove structure, a slide block and two flanges, wherein the crankshaft is provided with two eccentric parts along its axial direction; the crankshaft and the cylinder liner It is set eccentrically and the eccentric distance is fixed; the cross-slot structure is rotatably set in the cylinder liner. The cross-slot structure has two limit channels. The two limit channels are arranged sequentially along the axial direction of the crankshaft. The extension direction of the limit channels is vertical. in the axial direction of the crankshaft; the slide block has a through hole, there are two slide blocks, the two eccentric parts extend into the two through holes of the two slide blocks, and the two slide blocks are slidably arranged in the two limit channels And a variable volume cavity is formed. The variable volume cavity is located in the sliding direction of the slider. The crankshaft rotates to drive the slider to slide back and forth in the limit channel while interacting with the cross groove structure, so that the cross groove structure and the slider are in the cylinder liner. Rotation; two flanges are respectively provided at both axial ends of the cylinder liner. One of the two flanges has an air inlet channel, and the cylinder liner has a radial suction hole. The air inlet channel and the radial suction hole are connected to the two flanges respectively. The variable volume cavities are connected.

Optionally, the ratio S/V of the cross-sectional area S of the hole cross section of the air inlet channel to the displacement V of the fluid machine ranges from 0.001 to 0.6; the cross-sectional area S1 of the hole cross section of the radial suction hole and the The ratio S1/S between the cross-sectional areas S of the hole cross-sections ranges from 0.2 to 3.

Optionally, the inner wall surface of the cylinder liner has two suction chambers. The two suction chambers are spaced along the axial direction of the cylinder liner. The air inlet passage passes through the suction chamber and the variable volume chamber on the corresponding side of the two suction chambers. The radial suction holes are connected to the variable volume chamber through the suction chamber on the corresponding side of the two suction chambers.

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

Optionally, the air intake passage includes radial channel segments and axial channel segments that are connected in sequence, and the cylinder liner also has a suction communication cavity, and the suction communication cavity is only connected to the suction cavity used to communicate with the intake channel, The suction communication chamber extends a second preset distance along the axial direction of the cylinder liner, and one end of the suction communication chamber penetrates the axial end surface of the cylinder liner and communicates with the axial channel section.

Optionally, the air intake passage includes a radial channel segment and an axial channel segment that are connected in sequence. The cylinder liner also has a suction communication cavity. Both suction cavities are connected to the suction communication cavity. The suction communication cavity is connected along the cylinder. The axial direction of the sleeve extends a third preset distance, and one end of the suction communication cavity penetrates the axial end surface of the cylinder liner and is connected with the axial channel section.

Optionally, the position of the radial channel section in the circumferential direction of the flange is consistent with the position of the radial suction hole in the circumferential direction of the cylinder liner.

Optionally, the channel diameter D of the radial channel section is equal to the hole diameter D1 of the radial suction hole.

Optionally, the channel diameter D of the radial channel section is not equal to the hole diameter D1 of the radial suction hole.

Optionally, the relationship between the channel diameter D of the radial channel section and the skirt height H of the flange satisfies: ≥0.5mm.

Optional, the hole diameter D1 of the radial suction hole and the axial height H1 of the cylinder liner satisfy: ≥0.5mm.

Optionally, exhaust channels are provided on the end surfaces of the two flanges, and the two exhaust channels are respectively connected with the variable volume chambers on the corresponding sides.

Optionally, the end of the radial suction hole is the first compression inlet, the end of the inlet channel is the second compression inlet, and the initial ends of the two exhaust channels are both compression exhaust ports. When located at the radial When the slider on the side corresponding to the suction hole is in the air intake position, the first compression air inlet is connected to the corresponding variable volume chamber. When the slider on the side corresponding to the radial suction hole is in the exhaust position, the corresponding The variable volume chamber is connected to the compression exhaust port on the corresponding side; when the slider located on the corresponding side of the air inlet channel is in the air intake position, the second compression air inlet is connected to the corresponding variable volume cavity. When the slider is located on the corresponding side of the air inlet channel, When the slider on the corresponding side is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side.

Optionally, the fluid machinery is a compressor.

Optionally, the end of the radial suction hole is the first expansion exhaust port, the end of the air inlet channel is the second expansion exhaust port, and the initial ends of the two exhaust channels are both expansion inlets. When located at the radial When the slider on the side corresponding to the suction hole is in the air intake position, the first expansion exhaust port is connected to the corresponding variable volume chamber. When the slider on the side corresponding to the radial suction hole is in the exhaust position, the corresponding The variable volume chamber is connected to the expansion air inlet on the corresponding side; when the slider located on the corresponding side of the air intake channel is in the air intake position, the second expansion exhaust port is connected to the corresponding variable volume cavity. When the slider on the corresponding side is in the exhaust position, the corresponding variable volume chamber is connected to the expansion air inlet on the corresponding side.

Optionally, the fluid machinery is an expander.

Optionally, an exhaust chamber is provided on the outer wall of the cylinder liner, and the cylinder liner also has an exhaust port. The exhaust port is connected to the exhaust chamber from the inner wall of the cylinder liner. The fluid machine also includes an exhaust valve assembly, and the exhaust valve The component is arranged in the exhaust cavity and corresponding to the exhaust port.

Optionally, there are two exhaust ports, and the two exhaust ports are spaced along the axial direction of the cylinder liner. There are two exhaust valve assemblies, and the two exhaust valve assemblies are respectively provided corresponding to the two exhaust ports.

Optionally, at least one axial end face of the cylinder liner is also provided with a communication hole, which is connected with the exhaust chamber. Among the two flanges, the flange opposite to the communication hole is provided with an exhaust channel, and the communication hole is connected with the exhaust chamber. The air passages are connected.

Optionally, there is one exhaust port, and the exhaust port is connected to the variable volume chamber on the corresponding side. At least one axial end face of the cylinder liner is also provided with a connecting hole, and the connecting hole is connected to the exhaust chamber; two flanges A first exhaust channel is provided on the flange opposite to the communication hole, and the communication hole is connected with the first exhaust channel; among the two flanges, the flange on the side far from the exhaust port has a second exhaust channel, and the second exhaust channel is connected to the first exhaust channel. The exhaust channel is connected with the variable volume cavity on the corresponding side.

Optionally, the exhaust chamber extends through the outer wall of the cylinder liner, and the fluid machine also includes an exhaust cover plate, which is connected to the cylinder liner and seals the exhaust chamber.

Optionally, the end of the radial suction hole is the first compression inlet, the end of the intake channel is the second compression inlet, and the exhaust port on the cylinder liner is the compression exhaust port. When the slider on the side corresponding to the air hole is in the air intake position, the first compression air inlet is connected to the corresponding variable volume chamber. When the slider on the side corresponding to the radial suction hole is in the exhaust position, the corresponding variable volume chamber The second compression air inlet is connected to the corresponding variable volume cavity. When the slider located on the corresponding side of the air inlet channel is in the air intake position, the second compression air inlet is connected to the corresponding variable volume cavity. When the slider is located on the corresponding side of the air inlet channel, When the slider is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side.

Optionally, the fluid machinery is a compressor.

Optionally, the end of the radial suction hole is the first expansion exhaust port, the end of the intake channel is the second expansion exhaust port, and the exhaust port on the cylinder liner is the expansion inlet. When the slider on the side corresponding to the air hole is in the air intake position, the first expansion exhaust port is connected to the corresponding variable volume chamber. When the slider on the side corresponding to the radial suction hole is in the exhaust position, the corresponding variable volume chamber The cavity is connected to the expansion air inlet on the corresponding side; when the slider located on the corresponding side of the air inlet channel is in the air intake position, the second expansion exhaust port is connected with the corresponding variable volume cavity. When the slider is located on the corresponding side of the air inlet channel, When the slider is in the exhaust position, the corresponding variable volume chamber is connected to the expansion air inlet on the corresponding side.

Optionally, the fluid machinery is an expander.

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

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

Description of the drawings

In order to more clearly explain the technical solutions in the embodiments of the present application or the traditional technology, the drawings needed to be used in the description of the embodiments or the traditional technology will be briefly introduced below. Obviously, the drawings in the following description are only for the purpose of explaining the embodiments or the technical solutions of the traditional technology. For the embodiments of the application, those of ordinary skill in the art can also obtain other drawings based on the disclosed drawings without exerting creative efforts.

Figure 1 shows a schematic diagram of the internal structure of a fluid machine according to Embodiment 1 of the present application.

FIG. 2 shows a schematic structural diagram of the pump body assembly of the fluid machine in FIG. 1 .

FIG. 3 shows an exploded structural view of the pump body assembly in FIG. 2 .

Figure 4 shows a schematic diagram of the assembly structure of the crankshaft, cross groove structure, and slide block in Figure 3.

FIG. 5 shows a schematic cross-sectional structural view of the crankshaft, cross groove structure, and slide block in FIG. 4 .

FIG. 6 shows a schematic structural diagram of the shaft body part of the crankshaft in FIG. 3 and the eccentricity of the two eccentric parts.

FIG. 7 shows a schematic cross-sectional structural view of the assembly eccentricity of the crankshaft and cylinder liner in FIG. 3 .

Figure 8 shows a structural schematic diagram of the eccentricity between the cylinder liner and the lower flange in Figure 3.

FIG. 9 shows a schematic structural view of the slider in FIG. 3 in the axial direction of the through hole.

FIG. 10 shows a schematic structural view of the upper flange of the pump body assembly in FIG. 3 .

FIG. 11 shows a schematic cross-sectional structural view of the upper flange in FIG. 10 .

FIG. 12 shows a schematic structural view of the cylinder liner of the pump body assembly in FIG. 3 .

FIG. 13 shows a schematic cross-sectional structural view of the cylinder liner in FIG. 12 .

FIG. 14 shows a schematic cross-sectional structural view of the cylinder liner in FIG. 12 from another perspective.

Figure 15 shows a schematic structural diagram of the non-independent suction of the upper flange and cylinder liner of the pump body assembly in Figure 2.

Figure 16 shows a schematic diagram of the internal structure of a fluid machine according to Embodiment 2 of the present application.

FIG. 17 shows a schematic structural diagram of the pump body assembly of the fluid machine in FIG. 16 .

FIG. 18 shows an exploded structural view of the pump body assembly in FIG. 16 .

Fig. 19 shows a schematic structural diagram of the cylinder liner in Fig. 18.

FIG. 20 shows a schematic cross-sectional structural view of the cylinder liner in FIG. 19 .

Figure 21 shows a schematic structural view of the lower flange in Figure 18.

FIG. 22 shows a schematic cross-sectional structural view of the lower flange in FIG. 21 .

Figure 23 shows a schematic structural diagram of the non-independent suction of the lower flange and cylinder liner of the pump body assembly in Figure 17.

Figure 24 shows a schematic structural view of the upper flange and lower flange exhaust of the pump body assembly in Figure 17.

FIG. 25 shows a schematic structural diagram of the cylinder liner side exhaust of the pump body assembly in FIG. 17 .

Figure 26 shows a schematic structural diagram of the combination of cylinder liner side exhaust and flange exhaust of the pump body assembly in Figure 17.

27 is a graph showing the influence of the ratio of the cross-sectional area of the hole section of the air intake passage to the displacement of the fluid machine on the volumetric efficiency of the compressor.

Figure 28 shows a schematic diagram of the mechanism of compressor operation according to an optional embodiment of the present application.

Fig. 29 shows a schematic diagram of the mechanism of the operation of the compressor in Fig. 28.

Figure 30 shows a schematic diagram of the mechanism of compressor operation in the related art.

Figure 31 shows a schematic diagram of the mechanism of the improved compressor operation in the related art.

Figure 32 shows a schematic diagram of the mechanism of the operation of the compressor in Figure 31. In this figure, the force arm of the drive shaft driving the slider to rotate is shown.

Figure 33 shows a schematic diagram of the mechanism of operation of the compressor in Figure 31. In this figure, the center of the limiting groove structure coincides with the center of the eccentric portion.

Among them, the above-mentioned drawings include the following reference signs:

10. Crankshaft; 11. Eccentric part; 12. Shaft body part; 20. Cylinder liner; 21. Radial suction hole; 22. Exhaust port; 23. Suction chamber; 24. Suction connecting chamber; 25. Exhaust Air cavity; 26. Communication hole; 30. Cross groove structure; 31. Limiting channel; 40. Slider; 41. Through hole; 42. Extrusion surface; 50. Flange; 51. Exhaust channel; 511. Chapter One exhaust channel; 512, second exhaust channel; 52, upper flange; 53, lower flange; 54, air inlet channel; 541, radial channel section; 542, axial channel section; 80, liquid distributor Components; 81. Shell assembly; 82. Motor assembly; 83. Pump body assembly; 84. Upper cover assembly; 85. Lower cover assembly.

Detailed ways

The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only some of the embodiments of the present application, rather than all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by those of ordinary skill in the art without creative efforts fall within the scope of protection of this application.

In the related art, as shown in Figure 30, a compressor operating mechanism principle is proposed based on the cross slider mechanism, that is, point _O1 is used as the cylinder center, point _O2 is used as the drive shaft center, and point _O3 is used as the slider center. , the cylinder and the drive shaft are eccentrically arranged, in which the slider center O ₃ makes a circular motion on a circle with a diameter O ₁ O ₂ .

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

Since the midpoint O ₀ of the line segment O ₁ O ₂ is the virtual center, the balance system cannot be set up, which leads to the problem of deterioration of the high-frequency vibration characteristics of the compressor. Based on the above operating mechanism principle, as shown in Figure 31, a method is proposed A motion mechanism with O ₀ as the center of the drive shaft, that is, the cylinder center O ₁ and the drive shaft center O ₀ are the two rotation centers of the motion mechanism. The drive shaft has an eccentric part, the slider and the eccentric part are coaxially arranged, and the drive shaft is The assembly eccentricity of the cylinder is equal to the eccentricity of the eccentric part, so that the slider center _O3 makes a circular motion with the drive shaft center _O0 as the center and _O1O0 as the radius _.

Correspondingly, a set of operating mechanism is proposed, including a cylinder, a limit groove structure, a slider and a drive shaft. The limit groove structure is rotatably arranged in the cylinder, and the cylinder and the limit groove structure are coaxially arranged, that is, The center _O1 of the cylinder is also the center of the limit groove structure. The slider moves reciprocally relative to the limit groove structure. The slider is coaxially assembled with the eccentric part of the drive shaft. The slider makes circular motion around the shaft part of the drive shaft. 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 limiter. Bit slot structure rotation.

However, as shown in Figure 32, the length of the moment arm L of the drive shaft driving 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 groove.

As shown in Figure 33, when the cylinder center O ₁ (i.e., the center of the limiting groove structure) coincides with the center of the eccentric portion, the resultant force of the driving force of the drive shaft passes through the center of the limiting groove structure, that is, exerted on the limiting groove The torque on the groove structure is zero, and the limit groove structure cannot rotate. At this time, the motion mechanism is at a dead center position and cannot drive the slider to rotate.

Based on this, this application proposes a new cross-slot structure with two limit channels and a double slider mechanism principle, and builds a new compressor based on this principle, which has high energy efficiency and low noise. For small features, the following takes the compressor as an example to introduce in detail the fluid machinery based on the cross-groove structure with two limit channels and double sliders.

In order to solve the problems of low energy efficiency and high noise of compressors in related technologies, this application provides a fluid machinery, heat exchange equipment and an operating method of the fluid machinery, wherein the heat exchange equipment includes the following fluid machinery, The fluid machinery operates using the following operating methods.

The fluid machine in the embodiment of the present application includes a crankshaft 10, a cylinder liner 20, a cross groove structure 30 and a slider 40. The crankshaft 10 is provided with two eccentric parts 11 along its axial direction, and there is a third eccentric part 11 between the two eccentric parts 11. With a phase difference of an included angle A, the eccentricities of the two eccentric parts 11 are equal; the crankshaft 10 and the cylinder liner 20 are eccentrically arranged and the eccentric distance is fixed; the cross-slot structure 30 is rotatably disposed in the cylinder liner 20, and the cross-slot structure 30 has Two limiting channels 31 are arranged sequentially along the axial direction of the crankshaft 10 . The extending direction of the limiting channels 31 is perpendicular to the axial direction of the crankshaft 10 , and the extending direction of the two limiting channels 31 is between There is a phase difference of the second included angle B, where the first included angle A is twice the second included angle B; the slider 40 has a through hole 41, there are two sliders 40, and the two eccentric parts 11 extend in accordingly In the two through holes 41 of the two slide blocks 40, the two slide blocks 40 are slidably arranged in the two limiting channels 31 and form a variable volume cavity. The variable volume cavity is located in the sliding direction of the slide blocks 40, and the crankshaft 10 rotates. The slide block 40 is driven to slide back and forth in the limiting channel 31 while interacting with the cross groove structure 30 so that the cross groove structure 30 and the slide block 40 rotate in the cylinder liner 20 .

By arranging the cross groove structure 30 in a structural form with two limiting channels 31 and providing two slide blocks 40 correspondingly, the two eccentric parts 11 of the crankshaft extend into the two through holes 41 of the two slide blocks 40 correspondingly. , at the same time, the two sliders 40 are slidably arranged in the two limiting channels 31 and form a variable volume cavity, because the first included angle A between the two eccentric parts 11 is one of the extending directions of the two limiting channels 31 In this way, when one of the two sliders 40 is at the dead center position, that is, the driving torque of the eccentric portion 11 corresponding to the slider 40 at the dead center position is 0, the slider 40 at the dead center position cannot continue to rotate, and at this time, the driving torque of the other of the two eccentric parts 11 driving the corresponding slider 40 is the maximum value, ensuring the maximum driving torque. The eccentric part 11 can normally drive the corresponding slider 40 to rotate, thereby driving the cross groove structure 30 to rotate through the slider 40, and then driving the slider 40 at the dead center position to continue to rotate through the cross groove structure 30, realizing fluid flow. The stable operation of the machinery avoids the dead center position of the movement mechanism, improves the movement reliability of the fluid machinery, and ensures the working reliability of the heat exchange equipment.

In addition, because the fluid machinery provided by the embodiments of the present application can operate stably, that is, it ensures that the energy efficiency of the compressor is high and the noise is low, thereby ensuring the working reliability of the heat exchange equipment.

In the embodiment of the present application, neither the first included angle A nor the second included angle B is zero.

As shown in Figures 28 and 29, when the above-mentioned fluid machine is running, the crankshaft 10 rotates around the axis O ₀ of the crankshaft 10; the cross groove structure 30 revolves around the axis O ₀ of the crankshaft 10, and the axis O ₀ of the crankshaft 10 The first slider 40 makes a circular motion with the axis _O0 of the crankshaft ₁₀ as the center, and the center _O3 of the first slider 40 is in contact with the crankshaft. The distance between the axis O ₀ of the crankshaft 10 is equal to the eccentricity of the first eccentric portion 11 corresponding to the crankshaft 10 , and the eccentricity is equal to the eccentricity between the axis O ₀ of the crankshaft 10 and the axis O ₁ of the cross groove structure 30 distance, the crankshaft 10 rotates to drive the first slider 40 to perform circular motion, and the first slider 40 interacts with the cross groove structure 30 and slides back and forth in the limiting channel 31 of the cross groove structure 30; the second slider The block 40 makes a circular motion with the axis O ₀ of the crankshaft 10 as the center, and the distance between the center O ₄ of the second slide block 40 and the axis O ₀ of the crankshaft 10 is equal to the corresponding second eccentric part 11 of the crankshaft 10 The eccentricity is equal to the eccentricity distance between the axis O ₀ of the crankshaft 10 and the axis O ₁ of the cross groove structure 30 . The crankshaft 10 rotates to drive the second slider 40 to perform circular motion, and the second The slider 40 interacts with the cross groove structure 30 and slides back and forth in the limiting channel 31 of the cross groove structure 30 .

The fluid machine operated as described above constitutes a cross slider mechanism. This operating method adopts the principle of the cross slider mechanism, in which the two eccentric parts 11 of the crankshaft 10 serve as the first connecting rod L ₁ and the second connecting rod L ₂ respectively. , the two limiting channels 31 of the cross groove structure 30 serve as the third link L ₃ and the fourth link L ₄ respectively, and the lengths of the first link L ₁ and the second link L ₂ are equal (please refer to Figure 28 ).

As shown in Figure 28, there is a first included angle A between the first link L ₁ and the second link L ₂ , and a second included angle B between the third link L ₃ and the fourth link L ₄ . Among them, the first included angle A is twice the second included angle B.

As shown in Figure 29, the connection between the axis O ₀ of the crankshaft 10 and the axis O ₁ of the cross groove structure 30 is the connection line O ₀ O ₁ , and the connection between the first connecting rod L ₁ and the connection 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 connecting rod L ₃ and the connection line O ₀ O ₁ , where the third included angle C is twice the fourth included angle D; There is a 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 , where the fifth included angle Angle E is twice the sixth included angle F; the sum of the third included angle C and the fifth included angle E is the first included angle A, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

Further, the operation method also includes that the rotation angular speed of the slider 40 relative to the eccentric portion 11 is the same as the revolution angular speed of the slider 40 around the axis O ₀ of the crankshaft 10 ; the revolution angular speed of the cross groove structure 30 around the axis O ₀ of the crankshaft 10 This is the same as the rotation angular speed of the slider 40 relative to the eccentric portion 11 .

Specifically, the axis O ₀ of the crankshaft 10 is equivalent to the rotation center of the first connecting rod L ₁ and the second connecting rod L ₂ , and the axis O ₁ of the cross groove structure 30 is equivalent to the third connecting rod L _{3 and the fourth connecting rod L 3} . The rotation center of connecting rod L ₄ ; the two eccentric portions 11 of the crankshaft 10 serve as the first connecting rod L ₁ and the second connecting rod L ₂ respectively, and the two limiting channels 31 of the cross groove structure 30 serve as the third connecting rod L respectively. ₃ and the fourth connecting rod L ₄ , and the lengths of the first connecting rod L ₁ and the second connecting rod L ₂ are equal. In this way, when the crankshaft 10 rotates, the eccentric portion 11 on the crankshaft 10 drives the corresponding slider 40 around the crankshaft. The axis O of 10 revolves at ₀ , and at the same time the slider 40 can rotate relative to the eccentric part 11, and the relative rotation speed of the two is the same. Since the first slider 40 and the second slider 40 are in two corresponding limits respectively, The reciprocating movement in the position channel 31 drives the cross groove structure 30 to perform circular motion. Limited by the two limiting channels 31 of the cross groove structure 30, the movement direction of the two slide blocks 40 always has the phase of the second included angle B. difference, when one of the two sliders 40 is in the dead center position, the eccentric part 11 used to drive the other of the two sliders 40 has the maximum driving torque, and the eccentric part 11 with the maximum driving torque can The corresponding slider 40 is normally driven to rotate, thereby driving the cross groove structure 30 to rotate through the slider 40, and then driving the slider 40 at the dead center position to continue to rotate through the cross groove structure 30, achieving stable operation of the fluid machinery. It avoids the dead center position of the motion mechanism and improves the motion reliability of the fluid machinery, thus ensuring the working reliability of the heat exchange equipment.

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 has the axis O ₀ of the crankshaft 10 as the center and the connecting line O ₀ O ₁ as the radius.

In this application, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 times to complete 4 suction and exhaust processes.

In order to solve the problems of low energy efficiency and high noise of compressors in related technologies, the present application provides a fluid machine and heat exchange equipment, wherein the heat exchange equipment includes a fluid machine, and the fluid machine is the above-mentioned and following fluids. mechanical.

As shown in Figures 1 to 15, the fluid machine also includes a flange 50. The flange 50 is arranged at the axial end of the cylinder liner 20. The crankshaft 10 and the flange 50 are arranged concentrically. The cross groove structure 30 is concentric with the cylinder liner 20. The assembly eccentricity of the crankshaft 10 and the cross groove structure 30 is determined by the relative positional relationship between the flange 50 and the cylinder liner 20. The flange 50 is fixed on the cylinder liner 20 through fasteners, and the axis of the flange 50 is The relative position of the axis of the inner ring of the cylinder liner 20 is controlled by the alignment of the flange 50. The relative position of the axis of the flange 50 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 essence of adjusting the relative position of the axis through the flange 50 is to make the eccentricity of the eccentric portion 11 equal to the assembly eccentricity of the crankshaft 10 and the cylinder liner 20 .

Specifically, as shown in Figure 6, the eccentricities of the two eccentric parts 11 are equal to e. As shown in Figure 7, the assembly eccentricity between the crankshaft 10 and the cylinder liner 20 is e (due to the cross groove structure 30 and the cylinder liner 20 is coaxially arranged, the assembly eccentricity between the crankshaft 10 and the cross groove structure 30 is the assembly eccentricity between the crankshaft 10 and the cylinder liner 20), the flange 50 includes an upper flange 52 and a lower flange 53, as shown in Figure 8 As shown, the distance between the inner ring axis of the cylinder liner 20 and the inner ring axis of the lower flange 53 is e, 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 first assembly gap ranges from 0.005mm to 0.05mm.

Optionally, the first assembly gap ranges from 0.01 to 0.03 mm.

Optionally, the two slide blocks 40 are respectively arranged concentrically with the two eccentric parts 11. The slide blocks 40 make circular motion around the axis of the crankshaft 10. There is a first rotation gap between the hole wall of the through hole 41 and the eccentric part 11. The first rotation gap ranges from 0.005mm to 0.05mm.

Optionally, there is a second rotation gap between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder liner 20, and the size of the second rotation gap is 0.005 mm to 0.1 mm.

As shown in FIGS. 1 to 7 , the shaft portion 12 of the crankshaft 10 is integrally formed, and the shaft portion 12 has only one axis. This facilitates the one-time molding of the shaft portion 12 , thereby reducing the difficulty of processing and manufacturing the shaft portion 12 .

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 coaxially arranged, and the two eccentric portions 11 Set on the first and second paragraphs respectively.

Optionally, the first section and the second section are removably connected. In this way, the convenience of assembly and disassembly of the crankshaft 10 is ensured.

As shown in FIGS. 1 to 7 , the shaft body portion 12 of the crankshaft 10 and the eccentric portion 11 are integrally formed. This facilitates the one-time molding of the crankshaft 10 , thereby reducing the difficulty of processing and manufacturing the crankshaft 10 .

In an embodiment of the present application (not shown), the shaft portion 12 of the crankshaft 10 is detachably connected to the eccentric portion 11 . In this way, the installation and removal of the eccentric part 11 is facilitated.

As shown in FIGS. 3 and 4 , both ends of the limiting channel 31 penetrate to the outer peripheral surface of the cross groove structure 30 . In this way, it is helpful to reduce the difficulty of processing and manufacturing the cross groove structure 30 .

In this application, the first included angle A is 160 degrees to 200 degrees; the second included angle B is 80 degrees to 100 degrees. In this way, as long as the relationship that the first included angle A is twice the second included angle B is satisfied.

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

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

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

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

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

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

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

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

In this application, the eccentric portion 11 has an arc surface, and the central angle of the arc surface is greater than or equal to 180 degrees. In this way, it is ensured that the arc surface of the eccentric portion 11 can exert effective driving force on the slider 40 , thereby ensuring the movement reliability of the slider 40 .

As shown in Figures 1 to 7, the eccentric portion 11 is cylindrical.

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

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

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

In an embodiment of the present application (not shown), 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. 1 to 7 , the two eccentric portions 11 are spaced apart in the axial direction of the crankshaft 10 . In this way, during the process of assembling the crankshaft 10, the cylinder liner 20 and the two slide blocks 40, it is ensured that the distance between the two eccentric portions 11 can provide an assembly space for the cylinder liner 20 to ensure ease of assembly.

In this application, the cross groove structure 30 has a central hole, and the two limiting channels 31 are connected through the central hole. The diameter of the central hole is larger than the diameter of the shaft body portion 12 of the crankshaft 10 . In this way, it is ensured that the crankshaft 10 can pass through the center hole smoothly.

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

As shown in FIG. 9 , the axial projection of the slider 40 in the through hole 41 has two relatively parallel straight line segments and an arc segment connecting the ends of the two straight line segments. The limiting channel 31 has a set of oppositely arranged first sliding surfaces that are in sliding contact with the slider 40 . The slider 40 has a second sliding surface that cooperates with the first sliding surface. The slider 40 has a surface facing the limiting channel 31 The extrusion surface 42 at the end serves as the head of the slider 40. The two second sliding surfaces are connected through the extrusion surface 42, and the extrusion surface 42 faces the variable volume cavity. 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 pressing 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 Figure 9, the center of the through hole 41 of the slider 40 is 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. In Figure 9 The X dashed line represents 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, the radius of curvature of the arc surface and the radius of the inner circle of the cylinder liner 20 have a difference, and the difference ranges from -0.05mm to 0.025mm.

Optionally, the difference range is -0.02~0.02mm.

In this application, the relationship between the _{projected area S of the extrusion surface 42 in the sliding direction of the slider 40 and the area S row of the exhaust port 22 of the cylinder liner 20 satisfies: the value of S slider/S row is 8 ~} 25.

Optionally, the value of S _slider /S _row is 12~18.

The fluid machine shown in this embodiment is a compressor. As shown in Figure 1, the compressor includes a liquid dispenser component 80, a housing component 81, a motor component 82, a pump body component 83, an upper cover component 84 and a lower cover component 85. Among them, the dispenser component 80 is arranged outside the housing assembly 81, the upper cover assembly 84 is assembled on the upper end of the housing assembly 81, the lower cover assembly 85 is assembled on the lower end of the housing assembly 81, the motor assembly 82 and the pump body assembly 83 They are all located inside the housing assembly 81 , where the motor assembly 82 is located above the pump body assembly 83 , or the motor assembly 82 is located below the pump body assembly 83 . The pump body assembly 83 of the compressor includes the above-mentioned crankshaft 10, cylinder liner 20, cross groove structure 30, slide block 40, upper flange 52 and lower flange 53.

Further, as shown in FIG. 1 , the liquid dispenser component 80 has two suction pipes, and the two suction pipes are respectively used to communicate with the radial suction hole 21 and the air inlet channel 54 .

Optionally, the above components are connected by welding, thermal sheathing, or cold pressing.

The assembly process of the entire pump body assembly 83 is as follows: the lower flange 53 is fixed on the cylinder liner 20, the two slide blocks 40 are respectively placed in the two corresponding limit channels 31, and the two eccentric parts 11 of the crankshaft 10 are respectively extended into In the two corresponding through holes 41 of the two slide blocks 40, place the assembled crankshaft 10, the cross groove structure 30 and the two slide blocks 40 in the cylinder liner 20, and one end of the crankshaft 10 is installed on the lower flange 53 , the other end of the crankshaft 10 is disposed through the upper flange 52, see Figures 2 and 3 for details.

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. The pump body assembly 83 has a total of 4 variable volume chambers. In the volume chamber, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 times, and a single variable volume chamber completes one suction and exhaust process. For the compressor, the crankshaft 10 rotates 2 times, completing a total of 4 suction and exhaust processes.

Furthermore, the extrusion surface 42 of the head of the slider 40 , the two side wall surfaces and the bottom surface of the passage 31 , part of the inner wall surface of the cylinder liner 20 , and part of the surface of the upper flange 52 facing the cylinder liner 20 (or part of the surface of the lower flange 53 facing the cylinder liner 20 side) is a variable volume chamber.

In order to solve the problem of insufficient air suction of the compressor, this application adds the following content based on the above-mentioned fluid machinery, as follows:

Embodiment 1

As shown in Figures 1 to 15, the fluid machine also includes two flanges 50. The two flanges 50 are respectively provided at both axial ends of the cylinder liner 20. One of the two flanges 50 has an air inlet passage 54. The cylinder liner 20 has a radial suction hole 21, and the air inlet passage 54 and the radial suction hole 21 are respectively connected with two variable volume chambers.

One of the two flanges 50 is provided with an air inlet passage 54, and at the same time, the cylinder liner 20 is provided with a radial suction hole 21, and the air inlet passage 54 and the radial suction hole 21 are respectively connected with The two variable volume cavities are connected, thus ensuring the suction reliability of the fluid machine and avoiding suction loss due to insufficient suction of the fluid machine, thereby ensuring that the volumetric efficiency of the fluid machine can be optimized.

In addition, the air inlet passage 54 and the radial suction hole 21 are respectively provided on the flange 50 and the cylinder liner 20 to ensure that the compressor suction is sufficient, thereby improving the performance and cooling capacity of the compressor and solving the problem due to volume. Small size causes various structures to interfere with each other during design, making the design of the compressor easier.

In this embodiment, the upper flange 52 is provided with an air inlet channel 54 .

Optionally, the ratio S/V of the cross-sectional area S of the hole section of the air inlet channel 54 to the displacement V of the fluid machine ranges from 0.001 to 0.6; The ratio S1/S between the cross-sectional area S of the hole cross section of the channel 54 ranges from 0.2 to 3. In this way, by reasonably optimizing the range of the ratio S/V of the cross-sectional area S of the hole cross section of the radial suction hole 21 and the displacement V of the fluid machine, it is beneficial to reduce the insufficient suction of the compressor and the suction loss, thereby improving Compressor performance.

FIG. 27 is a graph showing the influence of the ratio of the cross-sectional area of the hole section of the air intake passage 54 to the displacement V of the fluid machine on the volumetric efficiency of the compressor. It can be seen from this figure that the volumetric efficiency of the compressor is optimal when the S/V range is between 0.001 and 0.6.

As shown in Figures 2, 13 and 15, the inner wall of the cylinder liner 20 has two suction chambers 23. The two suction chambers 23 are spaced along the axial direction of the cylinder liner 20. The air inlet passage 54 passes through the two suction chambers. The suction chamber 23 on the corresponding side of the two suction chambers 23 is connected to the variable volume chamber, and the radial suction hole 21 is connected to the variable volume chamber through the suction chamber 23 on the corresponding side of the two suction chambers 23 . In this way, it is ensured that the suction chamber 23 can store a large amount of gas, so that the variable volume chamber can be filled with suction, so that the compressor can suction a sufficient amount, and when suction is insufficient, the stored gas can be supplied to the compressor in time. Variable volume chamber to ensure the compression efficiency of the compressor.

Optionally, the suction chamber 23 is a cavity formed by being hollowed out in the radial direction on the inner wall surface of the cylinder liner 20. There may be one suction chamber 23, or there may be two upper and lower suction chambers.

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

As shown in Figures 2 and 11, the intake passage 54 includes a radial passage section 541 and an axial passage section 542 that are connected in sequence. The cylinder liner 20 also has a suction communication cavity 24, which is only used for The suction cavity 23 is connected with the intake passage 54 . The suction communication cavity 24 extends a second preset distance along the axial direction of the cylinder liner 20 , and one end of the suction communication cavity 24 penetrates the axial end surface of the cylinder liner 20 and is connected to the axial end surface of the cylinder liner 20 . Axial channel segments 542 communicate. In this way, the suction reliability of the intake passage 54 is ensured, and at the same time, the purpose of independent suction of the intake passage 54 and the radial suction hole 21 of the cylinder liner 20 is achieved, ensuring that the intake passage 54 and the radial suction hole 21 The inhalation process will not interfere with each other.

As shown in Figure 15, the intake passage 54 includes a radial passage section 541 and an axial passage section 542 that are connected in sequence. The cylinder liner 20 also has a suction communication cavity 24, and both suction cavities 23 are connected to the suction communication cavity. 24, the suction communication cavity 24 extends a third preset distance along the axial direction of the cylinder liner 20, and one end of the suction communication cavity 24 penetrates the axial end surface of the cylinder liner 20 and communicates with the axial channel section 542. In this way, the suction reliability of the intake passage 54 is ensured, and at the same time, the purpose of independent suction of the intake passage 54 and the radial suction hole 21 of the cylinder liner 20 is achieved.

When the displacements of the upper and lower parts of the cylinder liner 20 are not equal, suction can be performed through the non-independent suction method shown in Figure 15 to ensure sufficient suction of the compressor.

As shown in FIG. 3 , the position of the radial channel section 541 in the circumferential direction of the flange 50 is consistent with the position of the radial suction hole 21 in the circumferential direction of the cylinder liner 20 .

As shown in FIGS. 11 and 13 , the channel diameter D of the radial channel section 541 is equal to the hole diameter D1 of the radial suction hole 21 .

Of course, the channel diameter D of the radial channel section 541 and the hole diameter D1 of the radial suction hole 21 may also be different.

As shown in Figure 11, the relationship between the channel diameter D of the radial channel section 541 and the skirt height H of the flange 50 satisfies: H/2-D/2≥0.5mm. In this way, while ensuring sufficient suction of the compressor, the flange 50 is ensured to have sufficient structural strength.

As shown in Figure 13, the hole diameter D1 of the radial suction hole 21 and the axial height H1 of the cylinder liner 20 satisfy: H1/2-D1/2≥0.5mm. In this way, while ensuring sufficient air suction of the compressor, the cylinder liner 20 is ensured to have sufficient structural strength.

Embodiment 2

The difference between this embodiment and Embodiment 1 is that, as shown in Figures 16 to 23, the lower flange 53 in this embodiment is provided with an air inlet channel 54. The other features are similar and will not be described again here.

As shown in Figure 23, the intake passage 54 and the radial suction hole 21 of the cylinder liner 20 are non-independent suction. When the displacements of the upper and lower parts of the cylinder liner 20 are not equal, the non-independent suction in Figure 23 can be used. Suction air is used to ensure that the suction of the compressor is sufficient.

The following takes the compressor in Embodiment 2 as an example to describe the exhaust of the compressor:

Exhaust Embodiment 1, upper flange 52 and lower flange 53 perform flange exhaust:

As shown in Figure 24, exhaust channels 51 are provided on the end surfaces of the two flanges 50, and the two exhaust channels 51 are respectively connected with the variable volume chambers on the corresponding sides. In this way, the two exhaust channels 51 are respectively opened on the plane of the upper flange 52 and the lower flange 53 instead of the curved surface of the side wall of the cylinder liner 20 , which greatly reduces the difficulty of processing and manufacturing the exhaust channels 51 .

Taking the compressor as an example, the end of the radial suction hole 21 is the first compression inlet, the end of the inlet passage 54 is the second compression inlet, and the initial ends of the two exhaust passages 51 are both compressed exhaust. When the slider 40 located on the corresponding side of the radial suction hole 21 is in the air intake position, the first compression air inlet is connected to the corresponding variable volume chamber. When the slider 40 located on the corresponding side of the radial suction hole 21 40 is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side; when the slider 40 on the corresponding side of the air inlet passage 54 is in the air intake position, the second compression air inlet is connected to the corresponding compression exhaust port. The variable volume chamber is connected. When the slider 40 located on the corresponding side of the air inlet passage 54 is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side.

Other usage situations: This compressor can be used as an expander by exchanging the positions of the first compression air inlet, the second compression air inlet, and the compression exhaust port. That is, the compression exhaust port of the compressor is used as the suction port of the expander, high-pressure gas is introduced, and other pushing mechanisms rotate. After expansion, it passes through the first compression inlet (first expansion exhaust port) and second compression port of the compressor. The air inlet (second expansion exhaust port) discharges gas.

Specifically, the end of the radial suction hole 21 is the first expansion exhaust port, the end of the air inlet channel 54 is the second expansion exhaust port, and the initial ends of the two exhaust channels 51 are both expansion inlets. When the slider 40 on the side corresponding to the radial suction hole 21 is in the air intake position, the first expansion exhaust port is connected to the corresponding variable volume chamber. When the slider 40 on the side corresponding to the radial suction hole 21 is in the air intake position, In the exhaust position, the corresponding variable volume cavity is connected to the expansion air inlet on the corresponding side; when the slider 40 on the corresponding side of the air inlet passage 54 is in the air intake position, the second expansion exhaust port is connected to the corresponding variable volume cavity. The cavity is connected. When the slider 40 located on the corresponding side of the air inlet channel 54 is in the exhaust position, the corresponding variable volume cavity is connected with the expansion inlet on the corresponding side.

Optionally, the inner wall surface of the cylinder liner 20 has an expansion exhaust chamber, and the expansion exhaust chamber is connected with the expansion exhaust port.

Further, the expansion exhaust chamber extends a first preset distance around the circumference of the inner wall surface of the cylinder liner 20 to form an arc-shaped expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the expansion air inlet. One side extends, and the extension direction of the expansion exhaust chamber is in the same direction as the rotation direction of the cross groove structure 30 .

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

Further, the expansion exhaust communication chamber extends along the axial direction of the cylinder liner 20 for a second preset distance, and at least one end of the expansion exhaust communication chamber penetrates the axial end surface of the cylinder liner 20 .

Exhaust Example 2, exhaust from cylinder liner 20 side:

As shown in Figure 25, an exhaust chamber 25 is provided on the outer wall of the cylinder liner 20. The cylinder liner 20 also has an exhaust port 22. The exhaust port 22 is connected to the exhaust chamber 25 from the inner wall of the cylinder liner 20. The fluid machinery also has It includes an exhaust valve assembly, which is disposed in the exhaust chamber 25 and corresponding to the exhaust port 22 . In this way, the exhaust chamber 25 is used to accommodate the exhaust valve assembly, which effectively reduces the space occupied by the exhaust valve assembly, enables reasonable arrangement of components, and improves the space utilization of the cylinder liner 20 .

As shown in Figure 25, there are two exhaust ports 22, and the two exhaust ports 22 are spaced along the axial direction of the cylinder liner 20. There are two exhaust valve assemblies, and the two exhaust valve assemblies correspond to two exhaust ports respectively. Port 22 settings. In this way, since the two exhaust ports 22 are respectively provided with two sets of exhaust valve assemblies, a large amount of gas leakage in the variable volume chamber is effectively avoided and the compression efficiency of the variable volume chamber is ensured.

As shown in Figure 25, at least one axial end face of the cylinder liner 20 is also provided with a communication hole 26. The communication hole 26 is connected with the exhaust chamber 25. Among the two flanges 50, the flange 50 opposite to the communication hole 26 is provided with a communication hole 26. There is an exhaust channel 51, and the communication hole 26 communicates with the exhaust channel 51. In this way, the exhaust reliability of the cylinder liner 20 is ensured.

In this embodiment, the upper flange 52 is provided with an exhaust channel 51 . Of course, the lower flange 53 can also be provided with an exhaust channel 51 , or even both the upper flange 52 and the lower flange 53 can be provided with an exhaust channel 51 . The exhaust channel 51 can be selected according to needs.

Exhaust Embodiment 3: The exhaust on the cylinder liner 20 side is combined with one of the two flanges 50:

As shown in Figure 26, there is one exhaust port 22, and the exhaust port 22 is connected with the variable volume chamber on the corresponding side. A communication hole 26 is also provided on at least one axial end face of the cylinder liner 20, and the communication hole 26 is connected to the exhaust port. The cavity 25 is connected; the flange 50 of the two flanges 50 opposite to the communication hole 26 is provided with a first exhaust channel 511, and the communication hole 26 is connected to the first exhaust channel 511; the two flanges 50 are far away from the exhaust gas. The flange 50 on the port 22 side has a second exhaust channel 512, and the second exhaust channel 512 is connected with the variable volume chamber on the corresponding side. In this way, the purpose of exhausting the cylinder liner 20 side and exhausting the end face of one of the two flanges 50 is achieved, ensuring the exhaust reliability of the compressor.

In this application, the exhaust chamber 25 penetrates to the outer wall surface of the cylinder liner 20 , and the fluid machine also includes an exhaust cover plate, which is connected to the cylinder liner 20 and seals the exhaust chamber 25 . In this way, the exhaust cover serves to separate the variable volume chamber from the external space of the pump body assembly 83 .

Taking the compressor as an example, the end of the radial suction hole 21 is the first compression inlet, the end of the intake passage 54 is the second compression inlet, and the exhaust port 22 on the cylinder liner 20 is the compression exhaust port. , when the slider 40 located on the corresponding side of the radial suction hole 21 is in the air intake position, the first compression air inlet is connected to the corresponding variable volume chamber. When the slider 40 located on the corresponding side of the radial suction hole 21 When it is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side; when the slider 40 on the corresponding side of the air intake passage 54 is in the air intake position, the second compression air inlet is connected to the corresponding variable volume chamber. The volume chamber is connected. When the slider 40 located on the corresponding side of the air inlet passage 54 is in the exhaust position, the corresponding variable volume chamber is connected with the compression exhaust port on the corresponding side.

Other usage occasions: This compressor can be used as an expander by exchanging the positions of the first compression air inlet, the second compression air inlet, and the exhaust port. That is, the exhaust port of the compressor is used as the suction port of the expander, high-pressure gas is introduced, and other pushing mechanisms rotate. After expansion, it passes through the first compression inlet (first expansion exhaust port) and the second compression inlet of the compressor. The gas port (second expansion exhaust port) discharges gas.

Specifically, the end of the radial suction hole 21 is a first expansion exhaust port, the end of the intake passage 54 is a second expansion exhaust port, and the exhaust port 22 on the cylinder liner 20 is an expansion inlet. When When the slider 40 located on the side corresponding to the radial suction hole 21 is in the air intake position, the first expansion exhaust port is connected to the corresponding variable volume chamber. When the slider 40 located on the side corresponding to the radial suction hole 21 is in the exhaust position, When the slider 40 on the corresponding side of the air inlet passage 54 is in the air intake position, the second expansion exhaust port is connected to the corresponding variable volume cavity. When the slider 40 located on the corresponding side of the air inlet passage 54 is in the exhaust position, the corresponding variable volume chamber is connected to the expansion air inlet on the corresponding side.

It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular forms are also intended to include the plural forms unless the context clearly indicates otherwise. Furthermore, it will be understood that when the terms "comprises" and/or "includes" are used in this specification, they indicate There are features, steps, operations, means, components and/or combinations thereof.

The relative arrangement of components and steps, numerical expressions, and numerical values set forth in these examples do not limit the scope of the application unless specifically stated otherwise. At the same time, it should be understood that, for convenience of description, the dimensions of various parts shown in the drawings are not drawn according to actual proportional relationships. 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 are to be construed as illustrative only and not as limiting. Accordingly, other examples of the exemplary embodiments may have different values. It should be noted that similar reference numerals and letters refer to similar items in the following figures, so that once an item is defined in one figure, it does not need further discussion in subsequent figures.

For the convenience of description, spatially relative terms can be used here, such as "on...", "on...", "on the upper surface of...", "above", etc., to describe what is shown in the figure. The spatial relationship between one device or feature 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 a feature in the figure is turned upside down, then one feature described as "above" or "on top of" other features or features would then be oriented "below" or "below" the other features or features. under other devices or structures". Thus, the exemplary term "over" may include both orientations "above" and "below." The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular forms are also intended to include the plural forms unless the context clearly indicates otherwise. Furthermore, it will be understood that when the terms "comprises" and/or "includes" are used in this specification, they indicate There are features, steps, work, means, components and/or combinations thereof.

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

The technical features of the above-described embodiments can be combined in any way. To simplify the description, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, All should be considered to be within the scope of this manual.

The above-described embodiments only express several implementation modes of the present application, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the patent application. It should be noted that, for those of ordinary skill in the art, several modifications and improvements can be made without departing from the concept of the present application, and these all fall within the protection scope of the present application. Therefore, the protection scope of this patent application should be determined by the appended claims.

Claims (27)

1. A fluid machine, characterized by including:

   Crankshaft (10), the crankshaft (10) is provided with two eccentric parts (11) along its axial direction;

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

   Cross groove structure (30), the cross groove structure (30) is rotatably arranged in the cylinder liner (20), the cross groove structure (30) has two limiting channels (31), two The limiting channels (31) are arranged sequentially along the axial direction of the crankshaft (10), and the extension direction of the limiting channels (31) is perpendicular to the axial direction of the crankshaft (10);

   Slider (40), the slider (40) has a through hole (41), there are two sliders (40), and the two eccentric parts (11) correspondingly extend into the two sliders (41). In the two through holes (41) of 40), the two sliders (40) are slidably arranged in the two limiting channels (31) and form a variable volume cavity, and the variable volume cavity is located at In the sliding direction of the slider (40), the crankshaft (10) rotates to drive the slider (40) to reciprocate in the limiting channel (31) and interact with the cross groove structure (30). Function, causing the cross groove structure (30) and the slider (40) to rotate in the cylinder liner (20);

   Two flanges (50), the two flanges (50) are respectively provided at both axial ends of the cylinder liner (20), and one of the two flanges (50) has an air inlet channel ( 54), the cylinder liner (20) has a radial suction hole (21), and the air inlet passage (54) and the radial suction hole (21) are respectively connected with the two variable volume chambers.
2. The fluid machine according to claim 1, characterized in that the ratio S/V of the cross-sectional area S of the hole section of the air inlet channel (54) to the displacement V of the fluid machine ranges from 0.001 to 0.6;

   The ratio S1/S between the cross-sectional area S1 of the hole cross section of the radial suction hole (21) and the cross-sectional area S of the hole cross section of the air inlet passage (54) ranges from 0.2 to 3.
3. The fluid machine according to claim 1, characterized in that the inner wall surface of the cylinder liner (20) has two suction chambers (23), and the two suction chambers (23) are located along the cylinder liner (20). 20) are arranged at axial intervals, and the air inlet passage (54) is connected to the variable volume chamber through the suction chamber (23) on the corresponding side of the two suction chambers (23), and the diameter The suction hole (21) is connected to the variable volume chamber through the suction chamber (23) on the corresponding side of the two suction chambers (23).
4. The fluid machine according to claim 3, characterized in that the suction chamber (23) extends a first preset distance around the circumference of the inner wall surface of the cylinder liner (20) to form an arc-shaped suction chamber. (twenty three).
5. The fluid machine according to claim 3, characterized in that the air inlet passage (54) includes a radial passage section (541) and an axial passage section (542) that are connected in sequence, and the cylinder liner (20) It also has a suction communication cavity (24), which is only connected to the suction cavity (23) used to communicate with the air inlet passage (54). (24) Extend a second preset distance along the axial direction of the cylinder liner (20), and one end of the suction communication chamber (24) penetrates the axial end surface of the cylinder liner (20) and is connected with the shaft. Connected to channel segment (542).
6. The fluid machine according to claim 3, characterized in that the air inlet passage (54) includes a radial passage section (541) and an axial passage section (542) that are connected in sequence, and the cylinder liner (20) It also has a suction communication cavity (24), and both suction cavities (23) are connected with the suction communication cavity (24). The suction communication cavity (24) is along the cylinder liner (20). axially extends a third preset distance, and one end of the suction communication chamber (24) penetrates the axial end surface of the cylinder liner (20) and communicates with the axial channel section (542).
7. The fluid machine according to claim 5 or 6, characterized in that the position of the radial channel section (541) in the circumferential direction of the flange (50) is in the same position as the radial suction hole (21). The positions of the cylinder liner (20) in the circumferential direction are consistent.
8. The fluid machine according to claim 5 or 6, characterized in that the channel diameter D of the radial channel section (541) is equal to the hole diameter D1 of the radial suction hole (21).
9. The fluid machine according to claim 5 or 6, characterized in that the channel diameter D of the radial channel section (541) is not equal to the hole diameter D1 of the radial suction hole (21).
10. The fluid machine according to claim 5 or 6, characterized in that the relationship between the channel diameter D of the radial channel section (541) and the skirt height H of the flange (50) satisfies: (H/2 -D/2)≥0.5mm.
11. The fluid machine according to claim 5 or 6, characterized in that the hole diameter D1 of the radial suction hole (21) and the axial height H1 of the cylinder liner (20) satisfy: (H1/ 2-D1/2)≥0.5mm.
12. The fluid machine according to claim 1, characterized in that exhaust channels (51) are provided on the end surfaces of the two flanges (50), and the two exhaust channels (51) are connected to the corresponding side respectively. The variable volume cavity is connected.
13. The fluid machine according to claim 12, characterized in that the end of the radial suction hole (21) is a first compressed air inlet, and the end of the air inlet channel (54) is a second compressed air inlet. port, the initial ends of the two exhaust channels (51) are both compression exhaust ports,

    When the slider (40) located on the corresponding side of the radial suction hole (21) is in the air intake position, the first compression air inlet is connected to the corresponding variable volume chamber. When the slider (40) on the corresponding side of the radial suction hole (21) is in the exhaust position, the corresponding variable volume cavity is connected to the compression exhaust port on the corresponding side;

    When the slider (40) located on the corresponding side of the air intake passage (54) is in the air intake position, the second compression air inlet is connected to the corresponding variable volume chamber. When the slider (40) on the corresponding side of the air channel (54) is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side.
14. The fluid machine according to claim 13, characterized in that the fluid machine is a compressor.
15. The fluid machine according to claim 12, characterized in that the end of the radial suction hole (21) is a first expansion exhaust port, and the end of the air inlet channel (54) is a second expansion exhaust port. port, the initial ends of the two exhaust channels (51) are expansion air inlets,

    When the slider (40) located on the corresponding side of the radial suction hole (21) is in the air intake position, the first expansion exhaust port is connected to the corresponding variable volume chamber. When the slider (40) on the corresponding side of the radial suction hole (21) is in the exhaust position, the corresponding variable volume cavity is connected to the expansion air inlet on the corresponding side;

    When the slider (40) located on the corresponding side of the air intake passage (54) is in the air intake position, the second expansion exhaust port is connected to the corresponding variable volume chamber. When the slider (40) on the corresponding side of the air channel (54) is in the exhaust position, the corresponding variable volume cavity is connected to the expansion air inlet on the corresponding side.
16. The fluid machine according to claim 12, characterized in that the fluid machine is an expander.
17. The fluid machine according to claim 1, characterized in that an exhaust chamber (25) is provided on the outer wall of the cylinder liner (20), and the cylinder liner (20) also has an exhaust port (22). The exhaust port (22) is connected to the exhaust chamber (25) from the inner wall of the cylinder liner (20). The fluid machine also includes an exhaust valve assembly, and the exhaust valve assembly is disposed on the The exhaust chamber (25) is provided corresponding to the exhaust port (22).
18. The fluid machine according to claim 17, characterized in that there are two exhaust ports (22), and the two exhaust ports (22) are spaced apart along the axial direction of the cylinder liner (20), The exhaust valve assemblies are divided into two groups, and the two groups of exhaust valve assemblies are respectively provided corresponding to the two exhaust ports (22).
19. The fluid machine according to claim 18, characterized in that at least one axial end surface of the cylinder liner (20) is further provided with a communication hole (26), and the communication hole (26) is connected to the exhaust chamber. (25) are connected. Among the two flanges (50), the flange (50) opposite to the communication hole (26) is provided with an exhaust channel (51). The communication hole (26) is connected to the communication hole (26). The exhaust passages (51) are connected.
20. The fluid machine according to claim 17, characterized in that:

    There is one exhaust port (22), and the exhaust port (22) is connected to the variable volume chamber on the corresponding side. A communication hole is also provided on at least one axial end surface of the cylinder liner (20). (26), the communication hole (26) is connected with the exhaust chamber (25);

    Among the two flanges (50), the flange (50) opposite to the communication hole (26) is provided with a first exhaust channel (511), and the communication hole (26) is connected to the third exhaust channel (511). An exhaust channel (511) is connected; the flange (50) on the side away from the exhaust port (22) of the two flanges (50) has a second exhaust channel (512), and the The second exhaust channel (512) is connected with the variable volume chamber on the corresponding side.
21. The fluid machine according to claim 17, characterized in that the exhaust chamber (25) penetrates to the outer wall surface of the cylinder liner (20), the fluid machine further includes an exhaust cover, and the exhaust chamber The cover plate is connected to the cylinder liner (20) and seals the exhaust chamber (25).
22. The fluid machine according to any one of claims 17 to 21, characterized in that the end of the radial suction hole (21) is a first compression air inlet, and the end of the air inlet channel (54) is the second compression air inlet, and the exhaust port (22) on the cylinder liner (20) is a compression exhaust port,

    When the slider (40) located on the corresponding side of the radial suction hole (21) is in the air intake position, the first compression air inlet is connected to the corresponding variable volume chamber. When the slider (40) on the corresponding side of the radial suction hole (21) is in the exhaust position, the corresponding variable volume cavity is connected to the compression exhaust port on the corresponding side;

    When the slider (40) located on the corresponding side of the air intake passage (54) is in the air intake position, the second compression air inlet is connected to the corresponding variable volume chamber. When the slider (40) on the corresponding side of the air channel (54) is in the exhaust position, the corresponding variable volume chamber is connected to the compression exhaust port on the corresponding side.
23. The fluid machine according to claim 22, characterized in that the fluid machine is a compressor.
24. The fluid machine according to any one of claims 17 to 21, characterized in that the end of the radial suction hole (21) is a first expansion exhaust port, and the end of the air inlet channel (54) is the second expansion exhaust port, and the exhaust port (22) on the cylinder liner (20) is an expansion air inlet,

    When the slider (40) located on the corresponding side of the radial suction hole (21) is in the air intake position, the first expansion exhaust port is connected to the corresponding variable volume chamber. When the slider (40) on the corresponding side of the radial suction hole (21) is in the exhaust position, the corresponding variable volume cavity is connected to the expansion air inlet on the corresponding side;

    When the slider (40) located on the corresponding side of the air intake passage (54) is in the air intake position, the second expansion exhaust port is connected to the corresponding variable volume chamber. When the slider (40) on the corresponding side of the air channel (54) is in the exhaust position, the corresponding variable volume cavity is connected to the expansion air inlet on the corresponding side.
25. The fluid machine according to claim 24, characterized in that the fluid machine is an expander.
26. The fluid machine according to claim 1, characterized in that there is a phase difference of a first included angle (A) between the two eccentric parts (11), and the eccentricity amounts of the two eccentric parts (11) are equal. , and there is a phase difference of a second included angle (B) between the extension directions of the two limiting channels (31), wherein the first included angle (A) is the second included angle (B) twice.
27. A heat exchange equipment, including a fluid machine, characterized in that the fluid machine is the fluid machine according to any one of claims 1 to 26.

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