WO2023226407A1 - 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) in an axial direction of the crankshaft; 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), and the two eccentric portions (11) correspondingly extend into two through holes (41) of two sliding blocks (40); the cylinder sleeve (20) is provided with at least one radial air suction hole (21), the radial air suction hole (21) is used for being communicated with a variable volume cavity, and a ratio S/V of a cross-sectional area S of a hole cross section of a single radial air suction hole (21) to a discharge volume V of the fluid machine ranges from 0.006 to 0.01. The fluid machine ensures high volumetric efficiency thereof.

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 202210563924.7 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 fluid machinery, expanders, etc. Take fluid machinery 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. Fluid machinery, as the heart of the air conditioner, has a direct impact on the energy efficiency and noise level of the air conditioner. As the mainstream household air-conditioning fluid machinery, rolling rotor fluid machinery has become relatively mature after nearly a hundred years of development. However, it is limited by structural principles and has 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 and a slider. The crankshaft is provided with two eccentric parts along its axial direction; the crankshaft and the cylinder liner are eccentrically arranged with a fixed eccentric distance; The cross groove structure is rotatably arranged in the cylinder liner. The cross groove structure has two limiting channels. The two limiting channels are arranged sequentially along the axial direction of the crankshaft. The extension direction of the limiting channels is perpendicular to the axial direction of the crankshaft; the slider The block has a through hole, and there are two slide blocks. The two eccentric parts extend into the two through holes of the two slide blocks. The two slide blocks are slidably arranged in the two limit channels and form a variable volume cavity. The volume chamber 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, causing the cross groove structure and the slider to rotate in the cylinder liner; wherein, the cylinder liner has At least one radial suction hole, the radial suction hole is used to communicate with the variable volume cavity, and the ratio S/V of the cross-sectional area S of the single radial suction hole to the displacement V of the fluid machine is in the range of 0.006 ~0.01.

Optionally, the inner wall surface of the cylinder liner has a suction chamber, and the radial suction hole is connected to the variable volume chamber through the suction chamber.

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, there are two suction chambers. The two suction chambers are spaced along the axial direction of the cylinder liner. The cylinder liner also has a suction communication chamber. Both suction chambers are connected to the suction communication chamber. When the cylinder liner When there is one radial suction hole, the radial suction hole is connected to the two suction cavities through the suction communication cavity.

Optionally, the suction communication cavity extends a second preset distance along the axial direction of the cylinder liner, and at least one end of the suction communication cavity penetrates the axial end surface of the cylinder liner.

Optionally, the radial suction hole is symmetrical about the center line between the two axial end surfaces of the cylinder liner; the two suction chambers are symmetrical about the center line between the two axial end surfaces of the cylinder liner; suction The communication cavity includes two connected sub-suction communication cavities, and the two sub-suction communication cavities are symmetrical about the center line between the two axial end surfaces of the cylinder liner.

Optionally, the radial suction hole is asymmetrical with respect to the centerline between the two axial end surfaces of the cylinder liner; the two suction chambers are asymmetrical with respect to the centerline between the two axial end surfaces of the cylinder liner; The suction communication chamber includes two connected sub-suction communication chambers, and the two sub-suction communication chambers are asymmetrical with respect to the center line between the two axial end surfaces of the cylinder liner.

Optionally, based on the center line between the two axial end faces of the cylinder liner, the diameter of the cavity section of the sub-suction communicating cavity on the axis side of the radial suction hole is d1, and the diameter of the cavity section away from the radial suction hole is d1. The diameter of the cavity section of the sub-suction communicating cavity on the axis side of the air hole is d2, where d1<d2; the height of the suction cavity on the axis side of the radial suction hole in the axial direction of the cylinder liner is h1, the height of the suction chamber on the side of the axis away from the radial suction hole in the axial direction of the cylinder liner is h2, where h1 < h2.

Optionally, there are two suction chambers, the two suction chambers are spaced along the axial direction of the cylinder liner, and there are two radial suction holes, and the two radial suction holes correspond to the two suction chambers one by one. , and the two radial suction holes are connected to the corresponding variable volume chambers through the two suction cavities.

Optionally, the fluid machinery also includes two flanges. The two flanges are respectively provided at both axial ends of the cylinder liner. Exhaust channels are provided on the end faces of the two flanges. The two exhaust channels are respectively corresponding to The variable volume cavity on the side is connected.

Optionally, the end of the radial suction hole is the compression inlet, and the initial end of the exhaust channel is the compression exhaust port. When either slider is in the intake position, the compression inlet and the variable volume on the corresponding side The cavity is connected; when any slider is in the exhaust position, the variable volume cavity on the corresponding side is connected to the compression exhaust port.

Optionally, the fluid machinery is a compressor.

Optionally, the end of the radial suction hole is an expansion exhaust port, and the initial end of the exhaust channel is an expansion air inlet. When any slider is in the air intake position, the expansion exhaust port and the variable volume on the corresponding side The cavity is connected; when any slider is in the exhaust position, the variable volume cavity on the corresponding side is connected to the expansion air inlet.

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, there is one exhaust chamber, and a communication hole is provided on at least one axial end face of the cylinder liner. The communication hole is connected with the exhaust chamber. The fluid machine also includes two flanges, and the two flanges are respectively provided on the cylinder. At both axial ends of the sleeve, an exhaust channel is provided on the flange of the two flanges opposite to the communication hole, and the communication hole is connected with the exhaust channel.

Optionally, there are two exhaust ports, and the two exhaust ports are arranged at intervals along the axial direction of the cylinder liner. There are two exhaust chambers, and the two exhaust chambers and the two exhaust ports are arranged in one-to-one correspondence. The air valve assembly is composed of two groups, and the two groups of exhaust valve assemblies are respectively provided corresponding to the two exhaust ports.

Optionally, the two exhaust chambers are connected through an exhaust communication port, and a communication hole is also provided on at least one axial end face of the cylinder liner. The communication hole is connected to the exhaust chamber. The fluid machine also includes two flanges, two The flanges are respectively arranged at both axial ends of the cylinder liner. 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 channel.

Optionally, the two exhaust chambers are not connected, and communication holes are provided on both axial end faces of the cylinder liner. The two communication holes are connected to the two exhaust chambers respectively. The fluid machine also includes two flanges, two flanges. Two flanges are respectively provided at both axial ends of the cylinder liner. Exhaust channels are provided at positions where the two flanges are opposite to the communication holes. The communication holes are connected with the exhaust channels.

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 communication hole, and the communication hole is connected to the exhaust chamber; the fluid machine also includes Two flanges, the two flanges are respectively arranged at both axial ends of the cylinder liner. The flange opposite to the communication hole of the two flanges is provided with a first exhaust channel, and the communication hole is connected to the first exhaust channel. ; Among the two flanges, the flange on the side away from the exhaust port has a second exhaust channel, and the second 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 a compression air inlet, and the exhaust port on the cylinder liner is a compression exhaust port. When either slider is in the air intake position, the compression air inlet is connected to the variable speed on the corresponding side. The volume chamber is connected; when any slider is in the exhaust position, the variable volume chamber on the corresponding side is connected to the compression exhaust port.

Optionally, the fluid machinery is a compressor.

Optionally, the end of the radial suction hole is an expansion exhaust port, and the exhaust port on the cylinder liner is an expansion air inlet. When either slider is in the air intake position, the expansion exhaust port is in contact with the changer on the corresponding side. The volume chamber is connected; when any slider is in the exhaust position, the variable volume chamber on the corresponding side is connected to the expansion air inlet.

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, there is provided a heat exchange device 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 cross-sectional structural view of the symmetrical suction of the cylinder liner of the pump body assembly of the fluid machine in FIG. 2 .

FIG. 11 shows a schematic structural diagram of the suction path of the cylinder liner in FIG. 10 .

FIG. 12 shows a schematic cross-sectional structural view from the perspective of C-C in FIG. 10 .

FIG. 13 shows a schematic cross-sectional structural diagram from the D-D perspective in FIG. 10 .

FIG. 14 shows a schematic structural diagram of the cylinder liner of the fluid machine in FIG. 2 from a first perspective.

FIG. 15 shows a schematic structural view of the cylinder liner in FIG. 14 from a second perspective.

FIG. 16 shows a schematic structural view of the cylinder liner in FIG. 14 from a third perspective.

FIG. 17 shows a schematic structural diagram from the F-F perspective in FIG. 16 .

FIG. 18 shows a schematic structural diagram of the symmetrical suction path of the cylinder liner in FIG. 17 .

Figure 19 shows a schematic diagram of the internal structure of a fluid machine according to Embodiment 2 of the present application.

Figure 20 shows a schematic structural diagram of the pump body assembly of the fluid machine in Figure 19. In this figure, the cylinder liner is asymmetrically sucked.

Figure 21 shows a schematic structural diagram of a cylinder liner according to an optional embodiment of the present application.

FIG. 22 shows a schematic cross-sectional structural view from the G-G perspective in FIG. 21 .

FIG. 23 shows a schematic structural diagram of the asymmetric suction path of the cylinder liner in FIG. 22 .

FIG. 24 shows a schematic structural diagram of the cylinder liner in FIG. 19 .

FIG. 25 shows a schematic structural diagram of the cylinder liner in FIG. 24 from a top view.

FIG. 26 shows a schematic structural diagram of the cylinder liner in FIG. 24 from a bottom perspective.

Figure 27 shows a schematic diagram of the internal structure of a fluid machine according to Embodiment 3 of the present application.

Figure 28 shows a schematic structural diagram of the pump body assembly of the fluid machine in Figure 27. In this figure, the cylinder liner has symmetrical double suction.

Figure 29 shows a schematic structural diagram of a cylinder liner according to an optional embodiment of the present application.

FIG. 30 shows a schematic structural diagram of the cylinder liner in FIG. 29 from another perspective.

FIG. 31 shows a schematic structural view of the cylinder liner in FIG. 29 from a top view.

FIG. 32 shows a schematic cross-sectional structural view from the H-H perspective in FIG. 31 .

Fig. 33 shows a schematic diagram of the suction path of the symmetrical double suction of the cylinder liner in Fig. 32.

Figure 34 shows a schematic diagram of the exhaust structure of a pump body assembly of a fluid machine according to an optional embodiment of the present application.

Figure 35 shows a schematic structural view of the upper flange and the lower flange of the pump body assembly in Figure 34.

Figure 36 shows a schematic structural view of the cylinder liner of the pump body assembly in Figure 34.

Figure 37 shows a schematic diagram of the exhaust structure of a pump body assembly of a fluid machine according to another optional embodiment of the present application.

Figure 38 shows a schematic structural view of the upper flange of the pump body assembly in Figure 37.

Figure 39 shows a schematic structural view of the cylinder liner of the pump body assembly in Figure 37.

Figure 40 shows a schematic diagram of the mechanism of fluid machinery operation according to an optional embodiment of the present application.

Fig. 41 shows a schematic diagram of the mechanism of the operation of the fluid machine in Fig. 40.

FIG. 42 shows a schematic diagram of the mechanism of fluid machinery operation in the related art.

Figure 43 shows a schematic diagram of the mechanism of the improved fluid machinery operation in the related art.

Figure 44 shows a schematic diagram of the mechanism of the operation of the fluid machine in Figure 43. In this figure, the force arm of the drive shaft driving the slider to rotate is shown.

Figure 45 shows a schematic diagram of the mechanism of the operation of the fluid machine in Figure 43. In this figure, the center of the limiting groove structure coincides with the center of the eccentric portion.

Figure 46 shows the influence of the ratio of the cross-sectional area S of the hole cross section of the radial suction hole to the displacement V of the fluid machine on the volumetric efficiency of the fluid machine.

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; 27. Oblique cut; 28. Exhaust communication port; 30. Cross groove structure; 31. Limiting channel; 311. Variable volume cavity; 32. Center hole; 40. Slider; 41. Through hole; 42, extrusion surface; 50, flange; 51, exhaust channel; 511, first exhaust channel; 512, second exhaust channel; 52, upper flange; 53, lower flange; 60, Exhaust valve assembly; 70. Exhaust cover; 80. Dispenser components; 81. Shell assembly; 82. Motor assembly; 83. Pump body assembly; 84. Upper cover assembly; 85. Lower cover assembly; 90. fastener.

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 42, a fluid mechanical 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 fluid machinery. Based on the above operating mechanism principle, as shown in Figure 43, 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 44, 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 45, 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 limiting channels and a double slider mechanism principle, and builds a new fluid machine based on this principle, which has high energy efficiency and low noise. For small features, the following takes fluid machinery as an example to introduce in detail the fluid machinery based on a cross-groove structure with two limit channels and double sliders.

In order to solve the problems of low energy efficiency and high noise of fluid machinery in related technologies, this application provides a fluid machinery and heat exchange equipment, wherein the heat exchange equipment includes the above and following fluid machinery.

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 sliders 40, the two sliders 40 are slidably arranged in the two limiting channels 31 and form a variable volume cavity 311. The variable volume cavity 311 is located in the sliding direction of the slider 40. The crankshaft 10 rotates to drive the slider 40 to slide back and forth in the limiting channel 31 and interact with the cross groove structure 30 so that the cross groove structure 30 and the slider 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 311. Since the first included angle A between the two eccentric parts 11 is the extension direction of the two limiting channels 31 twice the second included angle B, so that 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. At this time, the driving torque of the other eccentric part 11 of the two eccentric parts 11 drives the corresponding slider 40 to the maximum value, ensuring the maximum driving rotation. The eccentric portion 11 of the moment 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, thus realizing The stable operation of the fluid machinery avoids the dead center position of the movement mechanism, improves the movement reliability of the fluid machinery, and thereby 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 fluid machinery has high energy efficiency and low noise, 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 40 and 41, 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 40 ).

As shown in Figure 40, 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 41, 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 O ₀ O ₁ , and the connection between the first connecting rod L ₁ and the connection 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.

As shown in Figures 1 to 39, the fluid machine also includes a flange 50. The flange 50 is disposed at the axial end of the cylinder liner 20. The crankshaft 10 and the flange 50 are concentrically disposed, and the cross groove structure 30 is concentric with the cylinder liner 20. Shaft setting, 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 the fastener 90, and the axis of the flange 50 The relative position to 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 to 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 the relative position of the axis center 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 Figures 2 to 7, 10, and 11, 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. 2 to 7 , 10 , and 11 , 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 to 5 , 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 2 to 7, 10, and 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 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. 2 to 7 , 10 , and 11 , 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.

As shown in FIG. 3 , the cross groove structure 30 has a central hole 32 , and the two limiting channels 31 are connected through the central hole 32 . The diameter of the central hole 32 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 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 pass through the center hole 32 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 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 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 projected area S of the extrusion surface 42 in the sliding direction of the slider 40 _slider and the area S row of the compression exhaust port 22 of the cylinder liner 20 satisfy: 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 fluid machine includes a 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 fluid machinery pump body assembly 83 includes the above-mentioned crankshaft 10, cylinder liner 20, cross groove structure 30, slide block 40, upper flange 52 and lower flange 53.

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 lower flange 53) is the variable volume chamber 311. The pump body assembly 83 has a total of four Variable volume chamber 311, when the crankshaft 10 rotates, the crankshaft 10 rotates 2 times, and a single variable volume chamber 311 completes one suction and exhaust process. For fluid machinery, the crankshaft 10 rotates 2 times, completing 4 suction and exhaust processes in total. gas process.

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 ) is the variable volume chamber 311 .

The following is a detailed introduction to the operation of fluid machinery:

As shown in Figure 1, the motor assembly 82 drives the crankshaft 10 to rotate, and the two eccentric portions 11 of the crankshaft 10 drive the corresponding two slide blocks 40 to move. When the slide blocks 40 revolve around the axis of the crankshaft 10, the slide blocks 40 Rotates relative to the eccentric part 11, and the slider 40 reciprocates along the limit channel 31, and drives the cross groove structure 30 to rotate in the cylinder liner 20. While the slider 40 revolves, it reciprocates along the limit channel 31 to form a cross slide. Block mechanism movement mode.

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

Embodiment 1

As shown in Figures 10 to 18 and 46, the cylinder liner 20 of the machine has at least one radial suction hole 21. The radial suction hole 21 is used to communicate with the variable volume chamber 311. A single radial suction hole 21 The ratio S/V of the cross-sectional area S of the hole section to the displacement V of the fluid machine ranges from 0.006 to 0.01.

By reasonably optimizing the ratio S/V of the cross-sectional area S of the radial suction hole 21 of the cylinder liner 20 to the displacement V of the fluid machine within the range of 0.006 to 0.01, the fluid machine is prevented from being damaged due to insufficient suction. This results in suction loss, thereby ensuring that the volumetric efficiency of the fluid machinery can be optimized within this range.

As shown in FIGS. 10 to 18 , the inner wall surface of the cylinder liner 20 has a suction chamber 23 , and the radial suction hole 21 communicates with the variable volume chamber 311 through the suction chamber 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 311 can be fully inhaled, so that the fluid machine can inhale a sufficient amount of air, and when the suction air is insufficient, the stored gas can be supplied in time. A variable volume chamber 311 is provided to ensure the compression efficiency of the fluid machine.

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 10 to 18, there are two suction chambers 23, and the two suction chambers 23 are spaced along the axial direction of the cylinder liner 20. The cylinder liner 20 also has a suction communication chamber 24, and the two suction chambers 23 Both are connected with the suction communication chamber 24. When the cylinder liner 20 has one radial suction hole 21, the radial suction hole 21 is connected with the two suction chambers 23 through the suction communication chamber 24. In this way, it is beneficial to increase the volume of the suction chamber 23, thereby reducing the suction pressure pulsation.

As shown in FIGS. 10 to 18 , the suction communication cavity 24 extends along the axial direction of the cylinder liner 20 for a second preset distance, and at least one end of the suction communication cavity 24 penetrates the axial end surface of the cylinder liner 20 . In this way, it is convenient to open the suction communication cavity 24 from the end surface of the cylinder liner 20, ensuring the convenience of processing the suction communication cavity 24.

As shown in Figures 10 to 18, the radial suction hole 21 is symmetrical about the center line between the two axial end surfaces of the cylinder liner 20; the two suction chambers 23 are symmetrical about the two axial end surfaces of the cylinder liner 20. The suction communication cavity 24 includes two connected sub-suction communication cavities, and the two sub-suction communication cavities are symmetrical about the center line between the two axial end surfaces of the cylinder liner 20 . In this way, it is ensured that the complete suction of the fluid machinery is sufficient, which is conducive to improving the performance and cooling capacity of the fluid machinery, solving the problem of mutual interference between the parts in the design caused by the small size of the fluid machinery, and ensuring the safety of the fluid machinery. Design is easier and ensures smooth and quiet operation of fluid machinery.

Embodiment 2

Considering that the displacements of the upper and lower parts of the cylinder liner 20 in the fluid machinery are not equal in the axial direction, the asymmetric suction method of the cylinder liner 20 can be used, as follows:

As shown in Figures 19 to 26, the radial suction hole 21 is asymmetrical with respect to the center line between the two axial end surfaces of the cylinder liner 20; the two suction chambers 23 are asymmetrical with respect to the two axial end surfaces of the cylinder liner 20. The centerline between the end faces is asymmetrical; the suction communication cavity 24 includes two connected sub-suction communication cavities, and the two sub-suction communication cavities are asymmetrical with respect to the centerline between the two axial end faces of the cylinder liner 20 . In this way, the vibration and noise generated during the operation of fluid machinery are solved through asymmetric design.

As shown in Figure 22, taking the center line between the two axial end faces of the cylinder liner 20 as a reference, the diameter of the cavity cross-section of the sub-suction communication cavity close to the axis side of the radial suction hole 21 is d1, The diameter of the cavity section of the sub-suction communication cavity on the side away from the axis of the radial suction hole 21 is d2, where d1<d2; the suction cavity 23 on the side of the axis close to the radial suction hole 21 is in the cylinder liner. The axial height of 20 is h1, and the height of the suction chamber 23 on the side of the axis away from the radial suction hole 21 in the axial direction of the cylinder liner 20 is h2, where h1 < h2. In this way, it is ensured that the problem of unequal displacement of the upper and lower parts of the cylinder liner 20 in the axial direction can be solved through the asymmetric suction mode of the cylinder liner 20 .

Embodiment 3

As shown in Figures 27 to 33, there are two suction chambers 23, and the two suction chambers 23 are spaced apart along the axial direction of the cylinder liner 20. There are two radial suction holes 21, and the two radial suction holes are 21 corresponds to the two suction chambers 23 one-to-one, and the two radial suction holes 21 are connected to the corresponding variable volume chambers 311 through the two suction chambers 23 respectively. In this way, it is ensured that the upper and lower parts of the cylinder liner 20 in the axial direction can form independent suction modes, ensuring that the two suction processes do not interfere with each other, and avoiding the problem that the upper and lower parts of the cylinder liner 20 in the axial direction are suctioning. During the process, the suction efficiency is reduced due to mutual interference.

In this embodiment, there are two radial suction holes 21, wherein the ratio S/V of the cross-sectional area S of the hole section of each radial suction hole 21 to the displacement V of the fluid machine is in the range of 0.006 to 0.01. .

The exhaust method of the fluid machine of the present application will be described below using the suction method in Embodiment 1. The following exhaust methods are applicable to the suction method fluid machines in Embodiment 2 and 3 above.

Exhaust Embodiment 1: The upper flange 52 and the lower flange 53 are exhausted respectively, as follows:

In an unillustrated embodiment of the present application, the fluid machine further includes two flanges 50 , the two flanges 50 are respectively provided at both axial ends of the cylinder liner 20 , and both flanges 50 have openings on their end surfaces. There is an exhaust channel 51, and the two exhaust channels 51 are respectively connected with the variable volume chamber 311 on the corresponding side. In this way, the upper and lower exhaust through the flange 50 replaces the related cylinder liner side exhaust. Since the side wall surface of the cylinder liner 20 is a curved surface, it is avoided that the exhaust passage 51 is opened on the curved cylinder liner 20, causing both sides to The two exhaust channels 51 are respectively opened on the planes of the upper flange 52 and the lower flange 53, which reduces the difficulty of processing and manufacturing the exhaust channels 51.

Specifically, the end of the radial suction hole 21 is a compression air inlet, and the initial end of the exhaust passage 51 is a compression exhaust port. When any slider 40 is in the air intake position, the compression air inlet is in contact with the corresponding side. The variable volume chamber 311 of the sliding block 40 is in the exhaust position, and the variable volume chamber 311 of the corresponding side is connected to the compression exhaust port. In this way, when the high-pressure gas enters the variable volume chamber 311 through the compressed air inlet, the high-pressure gas pushes the cross-slot structure 30 to rotate, and the cross-slot structure 30 rotates to drive the slider 40 to rotate, and at the same time, the slider 40 is relative to the cross-slot structure 30 slides linearly, thereby causing the slide block 40 to drive the eccentric portion 11 to rotate, that is, to drive the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can be made to output work.

Other usage occasions: This fluid machine exchanges the positions of the compression air inlet and compression exhaust port and can be used as an expander. That is, the compression exhaust port is used as the expander suction port, high-pressure gas is introduced, other pushing mechanisms rotate, and the gas is discharged through the compression inlet (expander exhaust port) after expansion.

Specifically, the end of the radial suction hole 21 is an expansion exhaust port, and the initial end of the exhaust passage 51 is an expansion air inlet. When any slider 40 is in the air intake position, the expansion exhaust port is in contact with the corresponding side. The variable volume chamber 311 of the slider 40 is in the exhaust position, and the variable volume chamber 311 of the corresponding side is connected to the expansion air inlet. In this way, when the high-pressure gas enters the variable volume chamber 311 through the expansion air inlet, the high-pressure gas pushes the cross-slot structure 30 to rotate, and the cross-slot structure 30 rotates to drive the slider 40 to rotate, and at the same time, the slider 40 is relative to the cross-slot structure 30 slides linearly, thereby causing the slide block 40 to drive the eccentric portion 11 to rotate, that is, to drive the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can be made to output work.

Exhaust Example 2, cylinder liner side exhaust, details are as follows:

As shown in Figures 34 to 36, 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 machine also includes an exhaust valve assembly 60 , 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 60, which effectively reduces the space occupied by the exhaust valve assembly 60, enables reasonable arrangement of components, and improves the space utilization of the cylinder liner 20.

As shown in Figures 34 to 36, 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 sets of exhaust valve assemblies 60, and the two sets of exhaust valve assemblies 60 are respectively Correspondingly two exhaust ports 22 are provided. In this way, since the two compression exhaust ports 22 are respectively provided with two sets of exhaust valve assemblies 60, a large amount of gas leakage in the variable volume chamber 311 is effectively avoided and the compression efficiency of the variable volume chamber 311 is ensured.

Further, the exhaust valve assembly 60 is connected to the cylinder liner 20 through fasteners. The exhaust valve assembly 60 includes an exhaust valve plate and a valve plate baffle. The exhaust valve plate is disposed in the exhaust chamber 25 and blocks the corresponding compression. For the exhaust port 22, the valve plate baffle is overlapped and arranged on the exhaust valve plate. In this way, the arrangement of the valve plate baffle effectively prevents the exhaust valve plate from excessively opening, thereby ensuring the exhaust performance of the cylinder liner 20 .

Optionally, the fasteners are screws.

In an embodiment of the present application (not shown), there is one exhaust chamber 25 , and a communication hole 26 is also provided on at least one axial end surface of the cylinder liner 20 . The communication hole 26 is connected to the exhaust chamber 25 , and the fluid machine also has It includes two flanges 50. The two flanges 50 are respectively arranged at both axial ends of the cylinder liner 20. 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 It is connected with the exhaust channel 51. In this way, the exhaust reliability of the cylinder liner 20 is ensured.

As shown in Figures 34 to 36, there are two exhaust ports 22, and the two exhaust ports 22 are spaced apart along the axial direction of the cylinder liner 20. There are two exhaust chambers 25, and the two exhaust chambers 25 are connected to the two exhaust chambers 25. The exhaust ports 22 are arranged in one-to-one correspondence, and the exhaust valve assemblies 60 are divided into two groups. The two groups of exhaust valve assemblies 60 are respectively arranged corresponding to the two exhaust ports 22 .

As shown in Figures 34 to 36, the two exhaust chambers 25 are connected through the exhaust communication port 28, and a communication hole 26 is also provided on at least one axial end surface of the cylinder liner 20. The communication hole 26 is connected with the exhaust chamber 25. The fluid machine also includes two flanges 50. The two flanges 50 are respectively provided at both axial ends of the cylinder liner 20. 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 communicates with the exhaust passage 51 . In this way, the exhaust from the cylinder liner 20 side is then transferred to the exhaust passage 51 of the upper flange 52 for exhaust.

In another not-shown embodiment of the present application, the two exhaust chambers 25 are not connected, and communication holes 26 are provided on both axial end surfaces of the cylinder liner 20. The two communication holes 26 are connected to the two rows respectively. The air chamber 25 is connected, and the fluid machine also includes two flanges 50. The two flanges 50 are respectively provided at both axial ends of the cylinder liner 20. The two flanges 50 are provided with exhaust holes at positions opposite to the communication hole 26. The passage 51 and the communication hole 26 are connected with the exhaust passage 51 . In this way, the upper and lower parts of the cylinder liner 20 perform side exhaust respectively, and then are converted to upper exhaust of the upper flange 52 , and then converted to lower exhaust of the lower flange 53 .

Exhaust Embodiment 3, cylinder liner side exhaust and flange end face exhaust, details are as follows:

As shown in Figures 37 to 39, there is one exhaust port 22, and the exhaust port 22 is connected with the variable volume chamber 311 on the corresponding side. At least one axial end surface of the cylinder liner 20 is also provided with a communication hole 26. The communication hole 26 is connected with the exhaust chamber 25; the fluid machine also includes two flanges 50, the two flanges 50 are respectively provided at both axial ends of the cylinder liner 20, and the flange 50 of the two flanges 50 is opposite to the communication hole 26. A first exhaust channel 511 is opened on the top, and the communication hole 26 is connected with the first exhaust channel 511; among the two flanges 50, the flange 50 on the side away from the exhaust port 22 has a second exhaust channel 512. The air channel 512 communicates with the variable volume chamber 311 on the corresponding side. In this way, side exhaust of the cylinder liner 20 is achieved combined with end exhaust of the flange 50 .

As shown in Figures 37 to 39, the exhaust chamber 25 penetrates to the outer wall surface of the cylinder liner 20. The fluid machine also includes an exhaust cover plate 70. The exhaust cover plate 70 is connected to the cylinder liner 20 and seals the exhaust chamber 25. In this way, the exhaust cover 70 serves to separate the variable volume chamber 311 from the external space of the pump body assembly 83 .

Specifically, the end of the radial suction hole 21 is a compression air inlet, and the exhaust port 22 on the cylinder liner 20 is a compression exhaust port. When any slider 40 is in the air intake position, the compression air inlet and The variable volume chamber 311 on the corresponding side is connected to the compression exhaust port; when any slider 40 is in the exhaust position, the variable volume chamber 311 on the corresponding side is connected to the compression exhaust port. In this way, when the high-pressure gas enters the variable volume chamber 311 through the compressed air inlet, the high-pressure gas pushes the cross-slot structure 30 to rotate, and the cross-slot structure 30 rotates to drive the slider 40 to rotate, and at the same time, the slider 40 is relative to the cross-slot structure 30 slides linearly, thereby causing the slide block 40 to drive the eccentric portion 11 to rotate, that is, to drive the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can be made to output work.

Other usage occasions: This fluid machine can be used as an expander by exchanging the positions of the suction and exhaust ports. That is, the compression exhaust port of the fluid machine is used as the expander suction port, high-pressure gas is introduced, other pushing mechanisms rotate, and the gas is discharged through the compression inlet (expander exhaust port) after expansion.

Specifically, the end of the radial suction hole 21 is an expansion exhaust port, and the exhaust port 22 on the cylinder liner 20 is an expansion air inlet. When any slider 40 is in the air intake position, the expansion exhaust port and The variable volume chamber 311 on the corresponding side is in communication; when any slider 40 is in the exhaust position, the variable volume chamber 311 on the corresponding side is in communication with the expansion air inlet. In this way, when the high-pressure gas enters the variable volume chamber 311 through the expansion air inlet, the high-pressure gas pushes the cross-slot structure 30 to rotate, and the cross-slot structure 30 rotates to drive the slider 40 to rotate, and at the same time, the slider 40 is relative to the cross-slot structure 30 slides linearly, thereby causing the slide block 40 to drive the eccentric portion 11 to rotate, that is, to drive the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can be made to output work.

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 .

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 the 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 (28)

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 (311). The volume chamber (311) is located in the sliding direction of the slider (40), and the crankshaft (10) rotates to drive the slider (40) to slide back and forth in the limiting channel (31) while intersecting with the The groove structure (30) interacts with each other, causing the cross groove structure (30) and the slider (40) to rotate in the cylinder liner (20);

   Wherein, the cylinder liner (20) has at least one radial suction hole (21), and the radial suction hole (21) is used to communicate with the variable volume chamber (311). A single radial suction hole (21) is used to communicate with the variable volume chamber (311). The ratio S/V of the cross-sectional area S of the hole cross section of the air hole (21) to the displacement V of the fluid machine ranges from 0.006 to 0.01.
2. The fluid machine according to claim 1, characterized in that the inner wall surface of the cylinder liner (20) has a suction chamber (23), and the radial suction hole (21) passes through the suction chamber (23). ) is connected with the variable volume chamber (311).
3. The fluid machine according to claim 2, 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).
4. The fluid machine according to claim 2, characterized in that 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 cylinder liner (20) also has a suction communication chamber (24), and both of the suction cavities (23) are connected to the suction communication chamber (24). When the cylinder liner (20) has a When the radial suction hole (21) is provided, the radial suction hole (21) communicates with the two suction cavities (23) through the suction communication cavity (24).
5. The fluid machine according to claim 4, wherein the suction communication chamber (24) extends a second preset distance along the axial direction of the cylinder liner (20), and the suction communication chamber (24) At least one end penetrates the axial end surface of the cylinder liner (20).
6. The fluid machine according to claim 4, characterized in that:

   The radial suction hole (21) is symmetrical about the center line between the two axial end surfaces of the cylinder liner (20);

   The two suction chambers (23) are symmetrical about the center line between the two axial end surfaces of the cylinder liner (20);

   The suction communication chamber (24) includes two connected sub-suction communication chambers, and the two sub-suction communication chambers are about the center line between the two axial end surfaces of the cylinder liner (20). symmetry.
7. The fluid machine according to claim 4, characterized in that:

   The radial suction hole (21) is asymmetrical with respect to the center line between the two axial end surfaces of the cylinder liner (20);

   The two suction chambers (23) are asymmetrical with respect to the center line between the two axial end surfaces of the cylinder liner (20);

   The suction communication chamber (24) includes two connected sub-suction communication chambers, and the two sub-suction communication chambers are about the center line between the two axial end surfaces of the cylinder liner (20). Asymmetrical.
8. The fluid machine according to claim 7, characterized in that, taking the center line between the two axial end surfaces of the cylinder liner (20) as a reference,

   The diameter of the cavity section of the sub-suction communication cavity on the side away from the axis of the radial suction hole (21) is d1, and the diameter of the sub-suction communication cavity on the side of the axis close to the radial suction hole (21) is d1. The diameter of the cavity cross-section of the suction communication cavity is d2, where d1<d2;

   The height of the suction chamber (23) on the axis side away from the radial suction hole (21) in the axial direction of the cylinder liner (20) is h1, and the height close to the radial suction hole (21) is h1. The height of the suction chamber (23) on the axis side of 21) in the axial direction of the cylinder liner (20) is h2, where h1<h2.
9. The fluid machine according to claim 2, characterized in that 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), There are two radial suction holes (21), and the two radial suction holes (21) correspond to the two suction cavities (23) one-to-one, and the two radial suction holes (21) correspond to the two suction cavities (23). The holes (21) are respectively connected with the corresponding variable volume chambers (311) through the two suction chambers (23).
10. The fluid machine according to claim 1, characterized in that the fluid machine further includes two flanges (50), and the two flanges (50) are respectively arranged in the axial direction of the cylinder liner (20). At both ends, 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 (311) on the corresponding side.
11. The fluid machine according to claim 10, characterized in that the end of the radial suction hole (21) is a compression air inlet, and the initial end of the exhaust passage (51) is a compression exhaust port,

    When any of the sliders (40) is in the air intake position, the compression air inlet is connected to the variable volume chamber (311) on the corresponding side;

    When any of the sliders (40) is in the exhaust position, the variable volume chamber (311) on the corresponding side is connected to the compression exhaust port.
12. The fluid machine according to claim 11, characterized in that the fluid machine is a compressor.
13. The fluid machine according to claim 10, characterized in that the end of the radial suction hole (21) is an expansion exhaust port, and the initial end of the exhaust passage (51) is an expansion inlet,

    When any of the sliders (40) is in the air intake position, the expansion exhaust port is connected to the variable volume chamber (311) on the corresponding side;

    When any of the sliders (40) is in the exhaust position, the variable volume chamber (311) on the corresponding side is in communication with the expansion air inlet.
14. The fluid machine according to claim 13, characterized in that the fluid machine is an expander.
15. 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 (60). The exhaust valve assembly (60) 60) is arranged in the exhaust chamber (25) and corresponding to the exhaust port (22).
16. The fluid machine according to claim 15, 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 assembly (60) is divided into two groups, and the two groups of exhaust valve assemblies (60) are respectively provided corresponding to the two exhaust ports (22).
17. The fluid machine according to claim 16, characterized in that there is one exhaust chamber (25), and a communication hole (26) is also provided on at least one axial end surface of the cylinder liner (20). The communication hole (26) communicates with the exhaust chamber (25). The fluid machine also includes two flanges (50). The two flanges (50) are respectively provided on the cylinder liner (20). At both axial ends, an exhaust channel (51) is provided on the flange (50) of the two flanges (50) opposite to the communication hole (26), and the communication hole (26) is connected to the communication hole (26). The exhaust passages (51) are connected.
18. The fluid machine according to claim 15, 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), There are two exhaust chambers (25), and the two exhaust chambers (25) and the two exhaust ports (22) are arranged in one-to-one correspondence. The exhaust valve assembly (60) has two exhaust chambers (25). The two groups of exhaust valve assemblies (60) are respectively provided corresponding to the two exhaust ports (22).
19. The fluid machine according to claim 18, characterized in that the two exhaust chambers (25) are connected through an exhaust communication port (28), and at least one axial end surface of the cylinder liner (20) is further provided with There is a communication hole (26) that communicates with the exhaust chamber (25). The fluid machine also includes two flanges (50), and the two flanges (50) are respectively provided. At both axial ends of the cylinder liner (20), an exhaust channel (51) is provided on the flange (50) of the two flanges (50) opposite to the communication hole (26). , the communication hole (26) communicates with the exhaust channel (51).
20. The fluid machine according to claim 18, characterized in that the two exhaust chambers (25) are not connected, and communication holes (26) are provided on both axial end faces of the cylinder liner (20). The two communication holes (26) are respectively connected with the two exhaust chambers (25). The fluid machine also includes two flanges (50), and the two flanges (50) are respectively provided at the respective exhaust chambers (25). Exhaust channels (51) are provided at both axial ends of the cylinder liner (20) and at the positions where the two flanges (50) are opposite to the communication hole (26). The communication hole (26) Communicated with the exhaust channel (51).
21. The fluid machine according to claim 15, characterized in that:

    There is one exhaust port (22), and the exhaust port (22) is connected to the variable volume chamber (311) on the corresponding side. At least one axial end surface of the cylinder liner (20) is also provided with There is a communication hole (26), and the communication hole (26) is connected with the exhaust chamber (25);

    The fluid machinery also includes two flanges (50). The two flanges (50) are respectively provided at both axial ends of the cylinder liner (20). The two flanges (50) are connected to A first exhaust channel (511) is provided on the flange (50) opposite to the communication hole (26), and the communication hole (26) is connected with the first exhaust channel (511); two The flange (50) on the side of the flange (50) away from the exhaust port (22) has a second exhaust channel (512), and the second exhaust channel (512) is connected to the corresponding side. The variable volume chamber (311) is connected.
22. The fluid machine according to claim 15, characterized in that the exhaust chamber (25) penetrates to the outer wall surface of the cylinder liner (20), and the fluid machine further includes an exhaust cover (70). The exhaust cover plate (70) is connected to the cylinder liner (20) and seals the exhaust chamber (25).
23. The fluid machine according to any one of claims 15 to 22, characterized in that the end of the radial suction hole (21) is a compression air inlet, and the exhaust port on the cylinder liner (20) The air port (22) is a compression exhaust port.

    When any of the sliders (40) is in the air intake position, the compression air inlet is connected to the variable volume chamber (311) on the corresponding side;

    When any of the sliders (40) is in the exhaust position, the variable volume chamber (311) on the corresponding side is connected to the compression exhaust port.
24. The fluid machine according to claim 23, characterized in that the fluid machine is a compressor.
25. The fluid machine according to any one of claims 15 to 22, characterized in that the end of the radial suction hole (21) is an expansion exhaust port, and the exhaust port on the cylinder liner (20) (22) is the expansion air inlet,

    When any of the sliders (40) is in the air intake position, the expansion exhaust port is connected to the variable volume chamber (311) on the corresponding side;

    When any of the sliders (40) is in the exhaust position, the variable volume chamber (311) on the corresponding side is in communication with the expansion air inlet.
26. The fluid machine according to claim 25, characterized in that the fluid machine is an expander.
27. 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.
28. 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 27.

Images