Fluid machine and heat exchange device

Abstract

The application provides a fluid machine and a heat exchange device. The fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure, a sliding block and two flanges. The crankshaft has two eccentric parts. The crankshaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed. The cross groove structure is rotatably arranged in the cylinder sleeve. Two limiting channels of the cross groove structure are sequentially arranged along the axial direction of the crankshaft. The extending direction of the limiting channel is perpendicular to the axial direction of the crankshaft. The two eccentric parts correspondingly extend into two through holes of the two sliding blocks. At least one of the two flanges is provided with an exhaust passage. The side wall surface of the cylinder sleeve is provided with two exhaust ports. The two exhaust ports are arranged at intervals along the axial direction of the cylinder sleeve and are both communicated with the exhaust passage. The cross-sectional area of the hole section of the exhaust port is S1. The volume of a single variable volume chamber is V1. 750≦V1 / S1≦3300. The application solves the problems of low energy efficiency, large noise and how to reduce exhaust loss of the compressor in the prior art.

Description

TECHNICAL FIELD

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

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

[0003] According to the national energy conservation and environmental protection policy and the comfort requirement of consumers for air conditioners, the air conditioning industry has been pursuing high efficiency and low noise. The compressor, as the heart of the air conditioner, has a direct impact on the energy efficiency and noise level of the air conditioner. The rolling rotor compressor, as the mainstream household air conditioner compressor, has been relatively mature after nearly a hundred years of development. Due to the limitation of the structure principle, the optimization space is limited. Therefore, it is urgent to propose a compressor with high energy efficiency, low noise and other characteristics.

[0004] In addition, the existing part of the compressor has a large exhaust loss, which leads to poor efficiency of the compressor. SUMMARY

[0005] The main purpose of the present application is to provide a fluid machine and a heat exchange device to solve the problems of low energy efficiency, large noise of the compressor in the prior art and how to reduce the exhaust loss.

[0006] In order to achieve the above-mentioned purpose, according to one aspect of the present application, a fluid machine is provided, comprising a crankshaft, a cylinder sleeve, a cross groove structure, a sliding block and two flanges, the crankshaft is provided with two eccentric parts along the axial direction thereof; the crankshaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve, the cross groove structure has two limiting channels, the two limiting channels are sequentially arranged along the axial direction of the crankshaft, and the extension direction of the limiting channel is perpendicular to the axial direction of the crankshaft; the sliding block has a through hole, and there are two sliding blocks, the two eccentric parts correspondingly extend into the two through holes of the two sliding blocks, the two sliding blocks are correspondingly arranged in the two limiting channels and form a variable volume chamber, the variable volume chamber is located in the sliding direction of the sliding block, and the crankshaft rotates to drive the sliding block to reciprocally slide in the limiting channel while interacting with the cross groove structure, so that the cross groove structure and the sliding block rotate in the cylinder sleeve; the two flanges are arranged at the two axial ends of the cylinder sleeve respectively, and at least one flange of the two flanges is provided with an exhaust passage; wherein, the side wall surface of the cylinder sleeve is provided with two exhaust ports, the two exhaust ports are arranged at intervals along the axial direction of the cylinder sleeve, and the two exhaust ports are in communication with the exhaust passage; the cross section area of the exhaust port hole cross section is S1, and the volume of a single variable volume chamber is V1, wherein 750≦V1 / S1≦3300.

[0007] Further, the positions of the two exhaust ports in the circumferential direction of the cylinder sleeve are consistent.

[0008] Further, the projection of the sliding block in the axial direction of the through hole has two opposite parallel straight line segments and an arc segment connecting the end portions of the two straight line segments; and the setting position of the exhaust port in the circumferential direction of the cylinder sleeve is within an angle range of (arccos(2R / B)~2*arccos(2R / B)), wherein R is the inner circle radius of the cylinder sleeve, and B is the distance between the two opposite parallel straight line segments of the projection of the sliding block in the axial direction of the through hole.

[0009] Further, the outer wall of the cylinder sleeve is provided with an exhaust cavity, the exhaust port is communicated to the exhaust cavity through the inner wall of the cylinder sleeve, and the fluid machine further comprises an exhaust valve assembly arranged in the exhaust cavity and corresponding to the exhaust port.

[0010] Further, the outer wall of the cylinder sleeve is provided with an exhaust cavity, the exhaust port is communicated to the exhaust cavity through the inner wall of the cylinder sleeve, and the fluid machine further comprises an exhaust valve assembly arranged in the exhaust cavity and corresponding to the exhaust port.

[0011] Further, the exhaust cavity is two, and the two exhaust cavities are arranged in the axial direction of the cylinder sleeve and are arranged and communicated one by one with the two exhaust ports.

[0012] Further, the two exhaust cavities are communicated through an exhaust communication hole, and the exhaust communication hole extends in the axial direction of the cylinder sleeve.

[0013] Further, the distance between the plane where the end of the exhaust port communicated with the exhaust cavity is located and the axis of the cylinder sleeve is K, and the inner circle radius of the cylinder sleeve is R, wherein 1mm≦K-R≦5mm.

[0014] Further, the cavity cross-sectional area of the exhaust cavity in the axial direction of the cylinder sleeve is S2, the height of a single exhaust cavity in the axial direction of the cylinder sleeve is M, and the displacement of the fluid machine is V, wherein 0.5≦ / V≦5.

[0015] Further, the outer wall of the cylinder sleeve is provided with an exhaust cavity, the cavity wall surface of the exhaust cavity is provided with a boss structure, and the exhaust port is communicated to the boss structure through the inner wall of the cylinder sleeve and is communicated with the exhaust cavity.

[0016] Further, the thickness of the boss structure in the extension direction of the exhaust port is N, wherein 0.05mm≦N≦3mm.

[0017] Further, the exhaust cavity penetrates to the outer wall surface of the cylinder sleeve, and the fluid machine further comprises an exhaust cover plate connected with the cylinder sleeve and sealing the exhaust cavity.

[0018] Further, the two eccentric portions have a phase difference of a first included angle A, the eccentric amounts of the two eccentric portions are equal, and the extension directions of the two limiting channels have a phase difference of a second included angle B, wherein the first included angle A is twice the second included angle B.

[0019] According to another aspect of the present application, there is provided a heat exchange device comprising a fluid machine, the fluid machine being the fluid machine described above.

[0020] According to the technical scheme of the present application, the exhaust passage is arranged on at least one of the two flanges; meanwhile, the side wall surface of the cylinder sleeve is provided with two exhaust ports, the two exhaust ports are arranged along the axial direction of the cylinder sleeve and are in communication with the exhaust passage; in addition, the cross-sectional area of the hole of the exhaust port is S1, the volume of the single variable volume chamber is V1, and 750≦V1 / S1≦3300, so that the exhaust reliability of the fluid machine is ensured, thereby reducing the exhaust loss of the fluid machine and improving the efficiency of the fluid machine. BRIEF DESCRIPTION OF DRAWINGS

[0021] The accompanying drawings, which form a part of the present application, are intended to provide further understanding of the present application, and are used to interpret the illustrative embodiments of the present application and their descriptions, and do not constitute improper limitations to the present application. In the drawings:

[0022] Figure 1 An internal structure schematic diagram of a compressor according to the embodiment one of the present application is shown;

[0023] Figure 2 A structure schematic diagram of a pump body assembly of the compressor in Figure 1 is shown;

[0024] Figure 3 An exploded structure schematic diagram of the pump body assembly in Figure 2 is shown;

[0025] Figure 4 An assembly structure schematic diagram of a crankshaft, a cross groove structure and a slider in Figure 3 is shown;

[0026] Figure 5 A sectional structure schematic diagram of the crankshaft, the cross groove structure and the slider in Figure 4 is shown;

[0027] Figure 6 A structure schematic diagram of the eccentricity of the shaft body part and the two eccentric parts of the crankshaft in Figure 4 is shown;

[0028] Figure 7 A sectional structure schematic diagram of the assembly eccentricity of the crankshaft and the cylinder sleeve in Figure 3 is shown;

[0029] Figure 8 A structure schematic diagram of the eccentricity between the cylinder sleeve and the lower flange in Figure 3 is shown;

[0030] Figure 9 A structure schematic diagram of the eccentricity between the cylinder sleeve and the lower flange inFigure 3 Structure diagram of the slider in the axial direction of the through hole;

[0031] Figure 10 Structure diagram of the slider in the axial direction of the through hole; Figure 3 Structure diagram of the compressor in the suction start state in the axial direction of the through hole;

[0032] Figure 11 Structure diagram of the compressor in the suction process in the axial direction of the through hole; Figure 3 Structure diagram of the compressor in the suction process in the axial direction of the through hole;

[0033] Figure 12 Structure diagram of the compressor in the suction end state in the axial direction of the through hole; Figure 3 Structure diagram of the compressor in the suction end state in the axial direction of the through hole;

[0034] Figure 13 Structure diagram of the compressor in the gas compression state in the axial direction of the through hole; Figure 3 Structure diagram of the compressor in the gas compression state in the axial direction of the through hole;

[0035] Figure 14 Structure diagram of the compressor in the exhaust process in the axial direction of the through hole; Figure 3 Structure diagram of the compressor in the exhaust process in the axial direction of the through hole;

[0036] Figure 15 Structure diagram of the compressor in the exhaust end state in the axial direction of the through hole; Figure 3 Structure diagram of the compressor in the exhaust end state in the axial direction of the through hole;

[0037] Figure 16 Structure diagram of the cylinder sleeve in the axial direction of the through hole; Figure 3 Structure diagram of the cylinder sleeve in the axial direction of the through hole;

[0038] Figure 17 Structure diagram of the cylinder sleeve in the axial direction of the through hole; Figure 3 Structure diagram of the cylinder sleeve in the axial direction of the through hole, showing the setting angle range of the exhaust port in the circumferential direction of the cylinder sleeve;

[0039] Figure 18 Structure diagram of the cylinder sleeve in the axial direction of the through hole, showing the relationship between K and R; Figure 3 Structure diagram of the cylinder sleeve in the axial direction of the through hole, showing the relationship between K and R;

[0040] Figure 19 Structure diagram of the cylinder sleeve in the axial direction of the through hole, showing the assembly eccentricity e between the crankshaft and the cylinder sleeve; Figure 2 Structure diagram of the cylinder sleeve in the axial direction of the through hole, showing the assembly eccentricity e between the crankshaft and the cylinder sleeve;

[0041] Figure 20 Structure diagram of the cylinder sleeve in the axial direction of the through hole, showing the assembly eccentricity e between the crankshaft and the cylinder sleeve; Figure 2 Structure diagram of the cylinder sleeve in the axial direction of the through hole, showing the assembly eccentricity e between the crankshaft and the cylinder sleeve;

[0042] Figure 21 Structure diagram of the cylinder sleeve in the axial direction of the through hole, showing the assembly eccentricity e between the crankshaft and the cylinder sleeve; Figure 3 Structure diagram of the cylinder sleeve in the axial direction of the through hole, showing the assembly eccentricity e between the crankshaft and the cylinder sleeve;

[0043] Figure 22 Fig. 4 shows a schematic view of the exhaust cavity side of the cylinder liner according to an alternative embodiment of the present application, in which a boss structure is provided at the exhaust port;

[0044] Figure 23 Fig. 5 shows a schematic view of a partial cross-sectional structure of the cylinder liner in Fig. 4; Figure 22

[0045] Figure 24 Fig. 6 shows a schematic view of a cross-section of the slider in Fig. 5 in the sliding direction thereof; Figure 3

[0046] Figure 25 Fig. 7 shows a schematic view of a pump body assembly according to a second embodiment of the present application;

[0047] Figure 26 Fig. 8 shows a schematic view of a pump body assembly according to a third embodiment of the present application;

[0048] Figure 27 Fig. 9 shows a schematic view of a pump body assembly according to a fourth embodiment of the present application;

[0049] Figure 28 Fig. 10 shows a schematic view of the mechanism principle of the compressor operation according to an alternative embodiment of the present application;

[0050] Figure 29 Fig. 11 shows a schematic view of the mechanism principle of the compressor operation in Fig. 10; Figure 28

[0051] Figure 30 Fig. 12 shows a schematic view of the mechanism principle of the compressor operation in the prior art;

[0052] Figure 31 Fig. 13 shows a schematic view of the mechanism principle of the improved compressor operation in the prior art;

[0053] Figure 32 Fig. 14 shows a schematic view of the mechanism principle of the compressor operation in Fig. 13, in which the force arm of the driving shaft driving the slider to rotate is shown; Figure 31

[0054] Fig. 15 shows a schematic view of the mechanism principle of the compressor operation in Fig. 14, in which the center of the limiting groove structure and the center of the eccentric part coincide; Figure 33 Figure 31 Fig. 16 shows a schematic view of the variation curves of the exhaust loss, COP and clearance volume of the compressor with V1 / S1.

[0055] Figure 34 Fig. 17 shows a schematic view of the variation curves of the exhaust loss, COP and clearance volume of the compressor with V1 / S1.

[0056] Fig. 18 shows a schematic view of the variation curves of the exhaust loss, COP and clearance volume of the compressor with V1 / S1.

[0057] ​​​​10, crankshaft; 11, eccentric part; 12, shaft body part;

[0058] 20, cylinder liner; 21, radial suction hole; 22, exhaust port; 23, suction chamber; 24, suction communication chamber; 25, exhaust chamber; 26, communication hole; 28, exhaust communication hole; 29, boss structure;

[0059] 30, cross groove structure; 31, limiting channel; 311, variable volume chamber; 32, center hole;

[0060] 40, slider; 41, through hole; 42, extrusion surface;

[0061] 50, flange; 51, exhaust passage; 52, upper flange; 53, lower flange;

[0062] 70, exhaust cover plate;

[0063] 80, distributor component; 81, housing assembly; 82, motor assembly; 83, pump body assembly; 84, upper cover assembly; 85, lower cover assembly. DETAILED DESCRIPTION

[0064] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. The description of the at least one exemplary embodiment is actually only illustrative, but not as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0065] In the prior art, as shown in Figure 30 , a compressor operating mechanism principle is proposed based on a cross slider mechanism, that is, taking point O1 as the center of the cylinder, point O2 as the center of the driving shaft, and point O3 as the center of the slider, the cylinder and the driving shaft are eccentrically arranged, wherein the slider center O3 makes a circular motion on a circle with a diameter of O1O2.

[0066] In the above operating mechanism principle, the cylinder center O1 and the driving shaft center O2 are the two rotation centers of the motion mechanism, and at the same time, the midpoint O0 of the line segment O1O2 is the virtual center of the slider center O3, so that the slider makes a reciprocating motion relative to the cylinder, and the slider also makes a reciprocating motion relative to the driving shaft.

[0067] Since the midpoint O0 of the line segment O1O2 is a virtual center, it is impossible to set a balance system, which leads to the problem of deterioration of the high-frequency vibration characteristics of the compressor. On the basis of the above operating mechanism principle, as shown in Figure 31As shown, a motion mechanism with O0 as the driving shaft center is proposed, that is, the cylinder center O1 and the driving shaft center O0 are two rotation centers of the motion mechanism, the driving shaft has an eccentric part, the slider is coaxially arranged with the eccentric part, and the assembly eccentricity of the driving shaft and the cylinder is equal to the eccentricity of the eccentric part, so that the slider center O3 makes a circular motion with the driving shaft center O0 as the center and O1O0 as the radius.

[0068] Correspondingly, a set of operation mechanism is proposed, which comprises a cylinder, a limiting groove structure, a slider and a driving shaft, wherein the limiting groove structure is rotatably arranged in the cylinder, and the cylinder and the limiting groove structure are coaxially arranged, that is, the cylinder center O1 is also the center of the limiting groove structure, the slider reciprocates relative to the limiting groove structure, the slider is coaxially assembled with the eccentric part of the driving shaft, and the slider makes a circular motion around the shaft body part of the driving shaft, and specifically, the motion process is as follows: the driving shaft rotates to drive the slider to revolve around the center of the shaft body part of the driving shaft, the slider simultaneously rotates relative to the eccentric part, and the slider reciprocates in the limiting groove of the limiting groove structure and drives the limiting groove structure to rotate.

[0069] However, as shown in the prior art, Figure 32 The length of the force arm L of the driving shaft driving the slider to rotate is L=2e*cos theta*cos theta, wherein e is the eccentricity of the eccentric part, and theta is the included angle between the O1O0 line and the sliding direction of the slider in the limiting groove.

[0070] As shown in the prior art, Figure 33 When the cylinder center O1 (that is, the center of the limiting groove structure) and the center of the eccentric part coincide, the resultant force of the driving force of the driving shaft passes through the center of the limiting groove structure, that is, the torque applied to the limiting groove structure is zero, and the limiting groove structure cannot rotate, at this time, the motion mechanism is in a dead point position and cannot drive the slider to rotate.

[0071] Based on this, the application proposes a completely new mechanism principle with a cross groove structure with two limiting channels and double sliders, and a completely new compressor is constructed based on the principle, which has the characteristics of high energy efficiency and low noise, and the compressor is taken as an example to specifically introduce the compressor based on the cross groove structure with two limiting channels and double sliders.

[0072] In order to solve the problems of low energy efficiency and large noise of the compressor in the prior art, the application provides a fluid machine, a heat exchange device and a running method of the fluid machine, wherein the heat exchange device comprises the fluid machine described below, and the fluid machine runs by using the running method described below.

[0073] The fluid machine in the application comprises a crankshaft 10, a cylinder sleeve 20, a cross groove structure 30 and a slider 40, wherein the crankshaft 10 is provided with two eccentric parts 11 along the axial direction of the crankshaft 10, the two eccentric parts 11 have a phase difference of a first included angle A, and the eccentricity of the two eccentric parts 11 is equal; the crankshaft 10 is eccentrically arranged with the cylinder sleeve 20 and the eccentric distance is fixed; the cross groove structure 30 is rotatably arranged in the cylinder sleeve 20, the cross groove structure 30 has two limiting channels 31, the two limiting channels 31 are sequentially arranged along the axial direction of the crankshaft 10, the extension direction of the limiting channel 31 is perpendicular to the axial direction of the crankshaft 10, and the extension directions of the two limiting channels 31 have a phase difference of a second included angle B, wherein the first included angle A is twice the second included angle B; the slider 40 has a through hole 41, and there are two sliders 40, the two eccentric parts 11 correspondingly extend into the two through holes 41 of the two sliders 40, the two sliders 40 are correspondingly arranged to slide 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, and when the crankshaft 10 rotates to drive the slider 40 to reciprocally slide in the limiting channel 31, the cross groove structure 30 and the slider 40 rotate in the cylinder sleeve 20.

[0074] By arranging the cross groove structure 30 in the form of two limiting channels 31 and correspondingly arranging two sliders 40, the two eccentric parts 11 of the crankshaft correspondingly extend into the two through holes 41 of the two sliders 40, and at the same time, the two sliders 40 are correspondingly arranged to slide in the two limiting channels 31 and form a variable volume cavity 311, since the first included angle A between the two eccentric parts 11 is twice the second included angle B between the extension directions of the two limiting channels 31, when one of the two sliders 40 is at the dead center position, the driving torque of the eccentric part 11 corresponding to the slider 40 at the dead center position is 0, and the slider 40 at the dead center position cannot continue to rotate, while the driving torque of the other eccentric part 11 of the two eccentric parts 11 driving the corresponding slider 40 is the maximum value, which ensures that the eccentric part 11 with the maximum driving torque can normally drive the corresponding slider 40 to rotate, thereby driving the cross groove structure 30 to rotate through the slider 40, and further driving the slider 40 at the dead center position to continue to rotate through the cross groove structure 30, realizing stable operation of the fluid machine, avoiding the dead center position of the motion mechanism, and improving the motion reliability of the fluid machine, thereby ensuring the working reliability of the heat exchange equipment.

[0075] In addition, the fluid machine provided by the application can stably operate, that is, the energy efficiency of the compressor is higher, the noise is smaller, and the working reliability of the heat exchange equipment is ensured.

[0076] It should be noted that in the application, the first included angle A and the second included angle B are not zero.

[0077] As Figure 28and Figure 29 As shown, when the aforementioned fluid machinery is running, the crankshaft 10 rotates around its axis O0; the cross-groove structure 30 revolves around the axis O0 of the crankshaft 10, with the axis O0 of the crankshaft 10 and the axis O1 of the cross-groove structure 30 being eccentrically positioned with a fixed eccentricity; the first slider 40 moves in a circular motion with the axis O0 of the crankshaft 10 as its center, and the distance between the center O3 of the first slider 40 and the axis O0 of the crankshaft 10 is equal to the eccentricity of the first eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentricity between the axis O0 of the crankshaft 10 and the axis O1 of the cross-groove structure 30. The crankshaft 10 rotates to drive the first slider 40 to move in a circular motion. The first slider 40 interacts with the cross groove structure 30 and slides back and forth within the limiting channel 31 of the cross groove structure 30; the second slider 40 makes a circular motion with the axis O0 of the crankshaft 10 as the center, and the distance between the center O4 of the second slider 40 and the axis O0 of the crankshaft 10 is equal to the eccentricity of the second eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentric distance between the axis O0 of the crankshaft 10 and the axis O1 of the cross groove structure 30. The crankshaft 10 rotates to drive the second slider 40 to make a circular motion, and the second slider 40 interacts with the cross groove structure 30 and slides back and forth within the limiting channel 31 of the cross groove structure 30.

[0078] The fluid machinery operating as described above constitutes a cross-slider mechanism. This operating method adopts the principle of a cross-slider mechanism, wherein the two eccentric portions 11 of the crankshaft 10 serve as the first connecting rod L1 and the second connecting rod L2, respectively, and the two limiting channels 31 of the cross groove structure 30 serve as the third connecting rod L3 and the fourth connecting rod L4, respectively, and the lengths of the first connecting rod L1 and the second connecting rod L2 are equal (please refer to...). Figure 28 ).

[0079] like Figure 29 As shown, there is a first included angle A between the first link L1 and the second link L2, and a second included angle B between the third link L3 and the fourth link L4, wherein the first included angle A is twice the second included angle B.

[0080] like Figure 29 As shown, the line connecting the axis O0 of crankshaft 10 and the axis O1 of cross groove structure 30 is line O0O1. The first connecting rod L1 has a third included angle C with line O0O1, and the corresponding third connecting rod L3 has a fourth included angle D with line O0O1, wherein the third included angle C is twice the fourth included angle D; the second connecting rod L2 has a fifth included angle E with line O0O1, and the corresponding fourth connecting rod L4 has a sixth included angle F with line O0O1, wherein the fifth included angle E is twice the sixth included angle F; the sum of the third included angle C and the fifth included angle E is the first included angle A, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

[0081] Further, the operation method further comprises that the rotation angular velocity of the slider 40 relative to the eccentric part 11 is the same as the revolution angular velocity of the slider 40 around the shaft center O0 of the crankshaft 10; and the revolution angular velocity of the cross-groove structure 30 around the shaft center O0 of the crankshaft 10 is the same as the rotation angular velocity of the slider 40 relative to the eccentric part 11.

[0082] Specifically, the shaft center O0 of the crankshaft 10 corresponds to the rotation center of the first connecting rod L1 and the second connecting rod L2, and the shaft center O1 of the cross-groove structure 30 corresponds to the rotation center of the third connecting rod L3 and the fourth connecting rod L4; the two eccentric parts 11 of the crankshaft 10 respectively serve as the first connecting rod L1 and the second connecting rod L2, and the two limiting channels 31 of the cross-groove structure 30 respectively serve as the third connecting rod L3 and the fourth connecting rod L4, and the lengths of the first connecting rod L1 and the second connecting rod L2 are equal, so that the crankshaft 10 rotates at the same time, the eccentric part 11 on the crankshaft 10 drives the corresponding slider 40 to revolve around the shaft center O0 of the crankshaft 10, and the slider 40 can rotate relative to the eccentric part 11 at the same time, and the relative rotation speeds of the two are the same, since the first slider 40 and the second slider 40 reciprocate in the two corresponding limiting channels 31 respectively, and drive the cross-groove structure 30 to move in a circle, limited by the two limiting channels 31 of the cross-groove structure 30, the movement directions of the two sliders 40 always have a phase difference of the second included angle B, when one of the two sliders 40 is at the dead point position, the eccentric part 11 for driving the other of the two sliders 40 has the maximum driving torque, the eccentric part 11 with the maximum driving torque can normally drive the corresponding slider 40 to rotate, so as to drive the cross-groove structure 30 to rotate through the slider 40, and then drive the slider 40 at the dead point position to continue to rotate through the cross-groove structure 30, so as to realize the stable operation of the fluid machine, avoid the dead point position of the movement mechanism, and improve the movement reliability of the fluid machine, so as to ensure the working reliability of the heat exchange equipment.

[0083] It should be noted that, in the present application, the maximum force arm of the driving torque of the eccentric part 11 is 2e.

[0084] Under the movement method, the running track of the slider 40 is a circle, and the circle has the shaft center O0 of the crankshaft 10 as the center and the line O0O1 as the radius.

[0085] It should be noted that, in the present application, in the process of the rotation of the crankshaft 10, the crankshaft 10 rotates 2 rounds, and completes 4 times of suction and exhaust processes.

[0086] In order to solve the problems of low energy efficiency and large noise of the compressor in the prior art, the present application provides a fluid machine and a heat exchange equipment, wherein the heat exchange equipment comprises the fluid machine, and the fluid machine is the fluid machine described above and below.

[0087] Embodiment one

[0088] As Figures 1 to 24 shown, the fluid machine further comprises a flange 50, the flange 50 is arranged at the axial end of the cylinder sleeve 20, the crankshaft 10 is arranged concentrically with the flange 50, the cross groove structure 30 is arranged coaxially with the cylinder sleeve 20, and the assembly eccentricity of the crankshaft 10 and the cross groove structure 30 is determined by the relative position relationship of the flange 50 and the cylinder sleeve 20, wherein the flange 50 is fixed on the cylinder sleeve 20 by fasteners, the relative position of the axis of the flange 50 and the axis of the inner ring of the cylinder sleeve 20 is controlled by centering the flange 50, and the relative position of the axis of the flange 50 and the axis of the inner ring of the cylinder sleeve 20 determines the relative position of the axis of the crankshaft 10 and the axis of the cross groove structure 30. The essence of centering the flange 50 is to make the eccentricity of the eccentric part 11 equal to the assembly eccentricity of the crankshaft 10 and the cylinder sleeve 20.

[0089] Specifically, as Figure 6 shown, the eccentricity of the two eccentric parts 11 is equal to e, as Figure 7 shown, the assembly eccentricity between the crankshaft 10 and the cylinder sleeve 20 is e (since the cross groove structure 30 is arranged coaxially with the cylinder sleeve 20, the assembly eccentricity between the crankshaft 10 and the cross groove structure 30 is the assembly eccentricity between the crankshaft 10 and the cylinder sleeve 20), and the flange 50 comprises an upper flange 52 and a lower flange 53, as Figure 8 shown, the distance between the axis of the inner ring of the cylinder sleeve 20 and the axis of the inner ring of the lower flange 53 is e, that is, equal to the eccentricity of the eccentric part 11.

[0090] Optionally, the first assembly gap between the crankshaft 10 and the flange 50 is 0.005mm-0.05mm.

[0091] Preferably, the first assembly gap is 0.01-0.03mm.

[0092] Optionally, the two sliders 40 are arranged concentrically with the two eccentric parts 11, the slider 40 makes circular motion around the axis of the crankshaft 10, and the first rotation gap between the hole wall of the through hole 41 and the eccentric part 11 is 0.005mm-0.05mm.

[0093] Optionally, the second rotation gap between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder sleeve 20 is 0.005mm-0.1mm.

[0094] As Figures 2 to 7 shown, the shaft body part 12 of the crankshaft 10 is integrally formed, and the shaft body part 12 has only one axis. In this way, the shaft body part 12 is formed at one time, thereby reducing the manufacturing difficulty of the shaft body part 12.

[0095] It should be noted that in an embodiment not shown in the drawings, the shaft portion 12 of the crankshaft 10 comprises a first segment and a second segment connected along an axial direction of the shaft portion 12, the first segment and the second segment are coaxially arranged, and the two eccentric portions 11 are arranged on the first segment and the second segment respectively.

[0096] Optionally, the first segment and the second segment are detachably connected. In this way, the assembly and disassembly of the crankshaft 10 are facilitated.

[0097] As shown in Figures 2 to 7 , the shaft portion 12 of the crankshaft 10 is integrally formed with the eccentric portions 11. In this way, the crankshaft 10 is formed at one time, thereby reducing the manufacturing difficulty of the crankshaft 10.

[0098] It should be noted that in an embodiment not shown in the drawings, the shaft portion 12 of the crankshaft 10 is detachably connected with the eccentric portions 11. In this way, the installation and disassembly of the eccentric portions 11 are facilitated.

[0099] As shown in Figure 3 and Figure 4 , both ends of the limiting channel 31 pass through to the outer circumferential surface of the cross groove structure 30. In this way, the manufacturing difficulty of the cross groove structure 30 is reduced.

[0100] It should be noted that in the present application, the first included angle A is 160-200 degrees; the second included angle B is 80-100 degrees. In this way, as long as the first included angle A is twice the second included angle B, the relationship is satisfied.

[0101] Preferably, the first included angle A is 160 degrees, and the second included angle B is 80 degrees.

[0102] Preferably, the first included angle A is 165 degrees, and the second included angle B is 82.5 degrees.

[0103] Preferably, the first included angle A is 170 degrees, and the second included angle B is 85 degrees.

[0104] Preferably, the first included angle A is 175 degrees, and the second included angle B is 87.5 degrees.

[0105] Preferably, the first included angle A is 180 degrees, and the second included angle B is 90 degrees.

[0106] Preferably, the first included angle A is 185 degrees, and the second included angle B is 92.5 degrees.

[0107] Preferably, the first included angle A is 190 degrees, and the second included angle B is 95 degrees.

[0108] Preferably, the first included angle A is 195 degrees, and the second included angle B is 97.5 degrees.

[0109] It should be noted that in the present application, the eccentric portion 11 has a circular arc surface, and the central angle of the circular arc surface is greater than or equal to 180 degrees. In this way, it is ensured that the circular arc surface of the eccentric portion 11 can exert an effective driving force on the slider 40, thereby ensuring the movement reliability of the slider 40.

[0110] As shown in Figures 2 to 7 , the eccentric portion 11 is cylindrical.

[0111] 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.

[0112] Optionally, the proximal end of the eccentric portion 11 protrudes from the outer circle of the shaft body portion 12 of the crankshaft 10.

[0113] 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.

[0114] It should be noted that in an embodiment of the present application not shown in the figure, the slider 40 comprises a plurality of sub-structures, which are spliced to form a through hole 41.

[0115] As shown in Figures 2 to 7 , the two eccentric portions 11 are arranged at intervals in the axial direction of the crankshaft 10. In this way, during assembly of the crankshaft 10, the cylinder sleeve 20 and the two sliders 40, it is ensured that the interval distance between the two eccentric portions 11 can provide assembly space for the cylinder sleeve 20, so as to ensure the assembly convenience.

[0116] As shown in Figure 3 , the cross groove structure 30 has a central hole 32, and the two limiting channels 31 are communicated through the central hole 32. The hole diameter of the central hole 32 is greater than the diameter of the shaft body portion 12 of the crankshaft 10. In this way, it is ensured that the crankshaft 10 can smoothly pass through the central hole 32.

[0117] Optionally, the hole diameter of the central hole 32 is greater than the diameter of the eccentric portion 11. In this way, it is ensured that the eccentric portion 11 of the crankshaft 10 can smoothly pass through the central hole 32.

[0118] As shown in Figure 9 , the projection of the slider 40 in the axial direction of the through hole 41 has two opposite parallel straight line segments and an arc line segment connecting the end portions of the two straight line segments. The limiting channel 31 has a set of oppositely arranged first sliding surfaces in sliding contact with the slider 40, the slider 40 has second sliding surfaces matched with the first sliding surfaces, the slider 40 has an extrusion surface 42 facing the end portion of the limiting channel 31, the extrusion surface 42 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 311. In this way, 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 extrusion surface 42 of the slider 40 in the axial direction of the through hole 41 is an arc line segment.

[0119] Specifically, the extrusion surface 42 is an arc surface, and the distance between the center of the arc surface and the center of the through hole 41 is equal to the eccentricity of the eccentric part 11. Figure 9 In the middle, the center of the through hole 41 of the slider 40 is O. 滑块 The distance between the center of the two arc surfaces and the center of the through hole 41 is 'e', ​​that is, the eccentricity of the eccentric part 11. Figure 9 The dashed X-line in the diagram represents the circle containing the center of the two arc surfaces.

[0120] Optionally, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20.

[0121] Optionally, the radius of curvature of the arc surface has a difference from the radius of the inner circle of the cylinder liner 20, and the difference ranges from -0.05mm to 0.025mm.

[0122] Preferably, the difference ranges from -0.02 to 0.02 mm.

[0123] It should be noted that in this application, the projected area S of the extrusion surface 42 in the sliding direction of the slider 40 is... 滑块 The area S of the compression exhaust port 22 of cylinder liner 20 排 The following conditions must be met between them: S 滑块 / S 排 The value is 8 to 25.

[0124] Preferably, S 滑块 / S 排 The value is 12 to 18.

[0125] It should be noted that the fluid machinery shown in this embodiment is a compressor, such as... Figure 1 As shown, the compressor includes a distributor component 80, a housing assembly 81, a motor assembly 82, a pump body assembly 83, an upper cover assembly 84, and a lower cover assembly 85. The distributor component 80 is located outside the housing assembly 81. The upper cover assembly 84 is mounted on the upper end of the housing assembly 81, and the lower cover assembly 85 is mounted on the lower end of the housing assembly 81. The motor assembly 82 and the pump body assembly 83 are both located inside the housing assembly 81, with the motor assembly 82 located either above or below the pump body assembly 83. The pump body assembly 83 of the compressor includes the aforementioned crankshaft 10, cylinder liner 20, cross-groove structure 30, slider 40, upper flange 52, and lower flange 53.

[0126] Alternatively, the above-mentioned components can be connected by welding, heat fitting, or cold pressing.

[0127] The assembly process of the whole pump body assembly 83 is as follows: the lower flange 53 is fixed on the cylinder sleeve 20, the two sliders 40 are respectively arranged in the two limiting channels 31, the two eccentric parts 11 of the crankshaft 10 are respectively inserted into the two through holes 41 of the two sliders 40, the assembled crankshaft 10, the cross groove structure 30 and the two sliders 40 are arranged in the cylinder sleeve 20, one end of the crankshaft 10 is arranged on the lower flange 53, and the other end of the crankshaft 10 passes through the upper flange 52, and specific reference can be made to Figure 2 and Figure 3 .

[0128] It should be noted that, in the embodiment, the closed space surrounded by the slider 40, the limiting channel 31, the cylinder sleeve 20 and the upper flange 52 (or the lower flange 53) is the variable volume chamber 311, and the pump body assembly 83 has four variable volume chambers 311. In the process of rotating the crankshaft 10, the crankshaft 10 rotates twice, and the single variable volume chamber 311 completes one suction and exhaust process. For the compressor, the crankshaft 10 rotates twice, and a total of four suction and exhaust processes are completed.

[0129] Further, the closed space surrounded by the extrusion surface 42 of the head of the slider 40, the two side wall surfaces and the channel bottom surface of the limiting channel 31, part of the inner wall surface of the cylinder sleeve 20 and part of the surface of the upper flange 52 (or part of the surface of the lower flange 53) on the side facing the cylinder sleeve 20 is the variable volume chamber 311.

[0130] As shown in Figures 10 to 15 , in the process of reciprocating movement of the slider 40 in the limiting channel 31, the slider 40 rotates relative to the cylinder sleeve 20, Figures 10 to 12 In the process of rotating the slider 40 clockwise from 0 degrees to 180 degrees, the variable volume chamber 311 increases, and in the process of increasing the variable volume chamber 311, the variable volume chamber 311 is in communication with the suction chamber 23 of the cylinder sleeve 20. When the slider 40 rotates to 180 degrees, the volume of the variable volume chamber 311 reaches the maximum value, and at this time, the variable volume chamber 311 is disconnected from the suction chamber 23, thereby completing the suction operation, Figures 13 to 15 In the process of rotating the slider 40 clockwise from 180 degrees to 360 degrees, the variable volume chamber 311 decreases, and the slider 40 compresses the gas in the variable volume chamber 311. When the slider 40 rotates to the position where the variable volume chamber 311 is in communication with the compression exhaust port 22, and when the gas in the variable volume chamber 311 reaches the exhaust pressure, the exhaust valve piece of the exhaust valve assembly is opened, and the exhaust operation starts, and until the compression ends and enters the next cycle.

[0131] As shown in Figures 10 to 15 , the point marked as M is taken as the reference point of the relative movement between the slider 40 and the crankshaft 10, Figure 11This represents the process of slider 40 rotating clockwise from 0 degrees to 180 degrees. The angle of rotation of slider 40 is θ1, and the corresponding angle of rotation of crankshaft 10 is 2θ1. Figure 13 The diagram shows the process of slider 40 continuing to rotate clockwise from 180 degrees to 360 degrees. The rotation angle of slider 40 is 180° + θ2, and the corresponding rotation angle of crankshaft 10 is 360° + 2θ2. Figure 14 The diagram shows the process of slider 40 continuing to rotate clockwise from 180 degrees to 360 degrees, and the variable volume cavity 311 is connected to the compression exhaust port 22. The angle of rotation of slider 40 is 180°+θ3, and the corresponding angle of rotation of crankshaft 10 is 360°+2θ3. That is, when slider 40 rotates 1 revolution, the corresponding crankshaft 10 rotates 2 revolutions, where θ1 < θ2 < θ3.

[0132] The following is a detailed introduction to the operation of the compressor:

[0133] like Figure 1 As shown, the motor assembly 82 drives the crankshaft 10 to rotate. The two eccentric parts 11 of the crankshaft 10 drive the corresponding two sliders 40 to move. While the sliders 40 revolve around the axis of the crankshaft 10, the sliders 40 rotate relative to the eccentric parts 11. The sliders 40 reciprocate along the limiting channel 31 and drive the cross groove structure 30 to rotate inside the cylinder liner 20. The sliders 40 revolve along the limiting channel 31 while revolving, thus forming the cross slider mechanism motion mode.

[0134] To address the issue of reducing exhaust losses, this application employs exhaust from the cylinder liner 20 side to reduce compressor exhaust losses, as detailed below:

[0135] like Figures 1 to 24 , Figure 34 As shown, two flanges 50 are respectively provided at both ends of the cylinder liner 20 along the axial direction. At least one of the two flanges 50 is provided with an exhaust passage 51. Two exhaust ports 22 are provided on the side wall of the cylinder liner 20. The two exhaust ports 22 are spaced apart along the axial direction of the cylinder liner 20, and both exhaust ports 22 are connected to the exhaust passage 51. The cross-sectional area of ​​the exhaust port 22 is S1, and the volume of a single variable volume cavity 311 is V1, wherein 750≦V1 / S1≦3300.

[0136] By providing an exhaust passage 51 on at least one of the two flanges 50, and providing two exhaust ports 22 on the side wall of the cylinder liner 20, the two exhaust ports 22 are spaced apart along the axial direction of the cylinder liner 20, and both exhaust ports 22 are connected to the exhaust passage 51; in addition, the cross-sectional area of ​​the exhaust port 22 is S1, and the volume of a single variable volume cavity 311 is V1, wherein 750≦V1 / S1≦3300, the exhaust reliability of the fluid machinery is ensured, thereby reducing the exhaust loss of the fluid machinery and improving the efficiency of the fluid machinery.

[0137] Furthermore, the unit of S1 above is square millimeters, and the unit of V1 is cubic millimeters.

[0138] It should be noted that in this application, the ratio V1 / S1 is a numerical ratio without units, and the same applies below. In addition, since the volume of a single variable volume cavity 311 is a variable value, the range of V1 in 750≦V1 / S1≦3300 in this application is the maximum value of the ratio.

[0139] like Figure 34 As shown, COP refers to the performance of the compressor, that is, the ratio of the output cooling or heating capacity to the power consumed by the compressor.

[0140] It should be noted that, in this application, if Figure 24 As shown, the cross-sectional area of ​​the slider 40 in its sliding direction is S, as follows. Figure 19 As shown, the assembly eccentricity of the cross-slot structure 30 is e. According to the compressor operating principle, the volume of a single variable volume chamber 311 is V1 = 4eS, the working volume of the entire compressor is V, and V = 4V1 = 16eS. That is, the displacement of the compressor is 16eS, in cubic millimeters.

[0141] like Figure 16 and Figure 21 As shown, the two exhaust ports 22 are positioned circumferentially on the cylinder liner 20.

[0142] like Figure 2 , Figure 9 and Figure 17 As shown, the axial projection of slider 40 onto through hole 41 has two relatively parallel straight line segments and an arc segment connecting the ends of the two straight line segments; the exhaust port 22 is positioned in the circumferential direction of cylinder liner 20 within the angular range of (arccos(2R / B)~2×arccos2R / B), where R is the inner radius of cylinder liner 20 and B is the distance between the two relatively parallel straight line segments of the axial projection of slider 40 onto through hole 41. Thus, by rationally optimizing the circumferential position of exhaust port 22 on cylinder liner 20, it is beneficial to avoid over-compression or under-compression of the compressor. Figure 17The angle range of θ in the above formula is (arccos(2R / B)~2×arccos2R / B), that is, the exhaust port 22 can be arranged in the above range in the circumferential direction of the cylinder liner 20.

[0143] As shown in Figures 10 to 18 , the cylinder liner 20 is provided with an exhaust cavity 25 on the outer wall, and the exhaust port 22 is communicated to the exhaust cavity 25 by the inner wall of the cylinder liner 20. The fluid machine further comprises an exhaust valve assembly arranged in the exhaust cavity 25 and corresponding to the exhaust port 22. The exhaust valve assembly is two groups, and the two groups of exhaust valve assemblies are arranged corresponding to the two exhaust ports 22 respectively. In this way, the exhaust cavity 25 is used to accommodate the exhaust valve assembly, effectively reducing the occupied space of the exhaust valve assembly, so that the components are reasonably arranged, and the space utilization of the cylinder liner 20 is improved.

[0144] As shown in Figures 10 to 18 , the axial end surface of the cylinder liner 20 is further provided with a communication hole 26, and the communication hole 26 is communicated with the exhaust cavity 25. The communication hole 26 is communicated with the exhaust passage 51. In this way, the exhaust reliability of the cylinder liner 20 is ensured.

[0145] As shown in Figure 16 and Figure 21 , the exhaust cavity 25 is two, and the two exhaust cavities 25 are arranged in the axial direction of the cylinder liner 20. The two exhaust cavities 25 are arranged and communicated one by one corresponding to the two exhaust ports 22. In this way, it is beneficial to reduce the throttling loss, so as to improve the performance of the compressor.

[0146] As shown in Figure 16 , the two exhaust cavities 25 are communicated through the exhaust communication hole 28, and the exhaust communication hole 28 extends in the axial direction of the cylinder liner 20. In this way, the communication reliability of the two exhaust cavities 25 is ensured.

[0147] Further, as shown in Figure 2 , the exhaust cavity 25 penetrates to the outer wall surface of the cylinder liner 20, and the fluid machine further comprises an exhaust cover plate connected with the cylinder liner 20 and sealing the exhaust cavity 25. In this way, the exhaust cover plate 70 plays a role of separating the variable volume cavity 311 from the external space of the pump body assembly 83.

[0148] Optionally, the exhaust cover plate 70 is fixed on the cylinder liner 20 by a fastener.

[0149] Optionally, the fastener is a screw.

[0150] Optionally, the outer contour of the exhaust cover plate 70 is matched with the outer contour of the exhaust cavity 25.

[0151] As shown in Figure 18As shown in the figure, the distance between the plane where the one end of the exhaust port 22 communicating with the exhaust cavity 25 is located and the axis of the cylinder sleeve 20 is K, and the inner circle radius of the cylinder sleeve 20 is R, wherein, 1mm≦K-R≦5mm. In this way, by reasonably optimizing the value range of K-R, the reliability requirements of the compressor are met, on the one hand, avoiding the fact that the thinner the thickness of the cylinder sleeve wall at the exhaust port 22 is, the less the strength of the cylinder sleeve wall at the exhaust port 22 is, and the subsequent high-frequency impact of the valve plate in the exhaust valve assembly easily leads to the fracture of the cylinder sleeve wall at the exhaust port 22; on the other hand, it also avoids the fact that the thickness of the cylinder sleeve wall at the exhaust port 22 is too thick, although the strength of the cylinder sleeve wall at the exhaust port 22 can meet the requirements, but the clearance volume is increased, which leads to the increase of the energy efficiency reduction of the compressor.

[0152] As shown in the figure, Figure 20 and Figure 21 , the cavity cross-sectional area of the exhaust cavity 25 in the axial direction of the cylinder sleeve 20 is S2, the height of a single exhaust cavity 25 in the axial direction of the cylinder sleeve 20 is M, and the displacement of the fluid machine is V, wherein, 0.5≦M×S2 / V≦5. In this way, by reasonably optimizing the ratio range of the volume of the exhaust cavity 25 to the displacement V of the compressor (fluid machine), it is ensured that the exhaust cavity 25 can reduce the exhaust noise and reduce the oil circulation rate of the compressor when running at high speed, wherein the unit of S2 is square millimeter, and the unit of M is mm.

[0153] It should be noted that in the present embodiment, another optional embodiment can also be provided, as shown in the figure, Figure 22 and Figure 23 , the exhaust cavity 25 is provided on the outer wall of the cylinder sleeve 20, the boss structure 29 is provided on the cavity wall surface of the exhaust cavity 25, and the exhaust port 22 penetrates the inner wall of the cylinder sleeve 20 to the boss structure 29 and communicates with the exhaust cavity 25. In this way, the boss structure 29 is an outwardly convex structure, and the setting of the boss structure 29 is beneficial to reduce the opening loss of the exhaust valve plate of the exhaust valve assembly caused by the adhesion of lubricating oil.

[0154] Further, as shown in the figure, Figure 23 , the thickness of the boss structure 29 in the extension direction of the exhaust port 22 is N, wherein, 0.05mm≦N≦3mm. In this way, on the one hand, the thickness of the cylinder sleeve wall at the exhaust port 22 is increased, and the strength of the cylinder sleeve wall at this position is sufficient; on the other hand, the opening loss of the exhaust valve plate of the exhaust valve assembly can also be reduced.

[0155] As shown in the figure, Figure 2 , Figures 10 to 19As shown, the cylinder sleeve 20 has a radial suction hole 21 and a suction cavity 23 which communicates with the radial suction hole 21. In this way, it is ensured that the suction cavity 23 can store a large amount of gas, so that the variable volume cavity 311 can fully suck in gas, so that the compressor can fully suck in gas, and when the gas suction is insufficient, the stored gas can be supplied to the variable volume cavity 311 in time to ensure the compression efficiency of the compressor.

[0156] Optionally, the suction cavity 23 is a cavity formed by hollowing out the inner wall of the cylinder sleeve 20 in the radial direction. The suction cavity 23 can be one or two.

[0157] Specifically, the suction cavity 23 extends a first predetermined distance around the circumference of the inner wall of the cylinder sleeve 20 to form an arc-shaped suction cavity 23. In this way, it is ensured that the volume of the suction cavity 23 is large enough to store a large amount of gas.

[0158] As shown in Figure 2 , Figures 10 to 19 , the suction cavity 23 is two, the two suction cavities 23 are arranged in an axial direction of the cylinder sleeve 20, the cylinder sleeve 20 further has a suction communication cavity 24, the two suction cavities 23 are both in communication with the suction communication cavity 24, and the radial suction hole 21 is in communication with the suction cavity 23 through the suction communication cavity 24. In this way, it is beneficial to increase the volume of the suction cavity 23, thereby reducing the suction pressure pulsation.

[0159] Further, as shown in Figure 2 , the suction communication cavity 24 extends a second predetermined distance in the axial direction of the cylinder sleeve 20, and at least one end of the suction communication cavity 24 penetrates the axial end surface of the cylinder sleeve 20. In this way, it is convenient to open the suction communication cavity 24 from the end surface of the cylinder sleeve 20, and it is ensured that the suction communication cavity 24 is easy to process.

[0160] It should be noted that in the present embodiment, as shown in Figure 2 , the upper flange 52 is provided with an exhaust passage 51, and the two exhaust ports 22 are in communication with the exhaust passage 51 through the exhaust cavity 25 and the communication hole 26.

[0161] Embodiment Two

[0162] It should be noted that the difference between the present embodiment and Embodiment One is that, as shown in Figure 25 , the upper flange 52 and the lower flange 53 are both provided with an exhaust passage 51, and the exhaust port 22 on the upper side of the cylinder sleeve 20 is in communication with the exhaust passage 51 on the upper flange 52, and the exhaust port 22 on the lower side of the cylinder sleeve 20 is in communication with the exhaust passage 51 on the lower flange 53.

[0163] Embodiment Three

[0164] It should be noted that the difference between the present embodiment and Embodiment One is that, as shown in Figure 26As shown, the cylinder sleeve 20 has two radial air suction holes 21, and the two radial air suction holes 21 are arranged axially spaced apart along the cylinder sleeve 20, and the two radial air suction holes 21 are respectively communicated with the air suction cavities 23 on the corresponding side.

[0165] Embodiment Four

[0166] It should be noted that the difference between the present embodiment and the embodiment two is that, as shown in the figure, Figure 27 As shown, the cylinder sleeve 20 has two radial air suction holes 21, and the two radial air suction holes 21 are arranged axially spaced apart along the cylinder sleeve 20, and the two radial air suction holes 21 are respectively communicated with the air suction cavities 23 on the corresponding side.

[0167] Of course, in an embodiment of the present application which is not shown in the figure, the upper flange 52 and the lower flange 53 can also be used for air suction through the flanges 50, or one of the two flanges 50 is used for air suction and matched with the cylinder sleeve 20 for air suction.

[0168] 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 form is intended to include the plural form, unless the context clearly indicates otherwise, and it should also be understood that the terms "comprise" and / or "include" as used in the specification indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0169] The relative arrangement of components and steps, numerical expressions and values set forth in these embodiments do not limit the scope of the present application unless otherwise specifically stated. At the same time, it should be understood that the sizes of the various parts shown in the drawings are not drawn in accordance with the actual proportional relationship. The techniques, methods and devices known to those skilled in the relevant art can not be discussed in detail, but in appropriate cases, the techniques, methods and devices should be considered as part of the authorized specification. In all examples shown and discussed herein, any specific value should be interpreted as merely exemplary, and not as a limitation. Therefore, other examples of exemplary embodiments can have different values. It should be noted that similar reference numbers and letters represent similar items in the following drawings, so once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0170] For purposes of the description hereinafter, the terms "upper", "lower", "right", "left", "rear", "front", "vertical", "horizontal", and derivatives thereof shall relate to the application as it is oriented in the drawing figures. The terms "on", "above", "under", "below" and derivatives thereof shall relate to the application as it is oriented in the drawing figures. Where, for purposes of clarity, directional terms are used in the description, it should be understood that relative terms such as "above" and "below" and "up" and "down" are used to describe the relative positions for purposes of explanation only. Changes in both the recited position and the use of the terms will depend on the context in which it is used and on the position of the device being described. The terms "first", "second", "third", etc., as used herein do not denote any order, quantity, or importance, but rather are used to distinguish one element from another. The terms "a" and "an" and "the" and similar reference use in the context of the specification are to be construed to cover both the singular and the plural, unless otherwise indicated by context. The terms "comprising", "having", "including", and "containing" are to be construed as open-ended terms (i.e., meaning "including, but not limited to") unless otherwise noted. The terms "sub-portion" and "sub-portion" are to be construed as open-ended terms (i.e., meaning "including, but not limited to") unless otherwise noted.

[0171] It is to be understood that the terminology used herein is for the purpose of describing the particular embodiments only and is not intended to be limiting. As used herein, the singular form "a", "an" and "the" include plural references unless the context clearly dictates otherwise. As used herein, the term "and / or" includes any and all combinations of one or more of the associated listed terms. As used herein, the term "includes" means includes but not limited to, and the term "including" means including but not limited to.

[0172] It should be noted that the terms "first", "second", and so on as used herein are used to distinguish one element from another, and do not imply a particular order or sequence. It should be understood that the use of these terms is intended to be interchangeable. It is to be understood that the terminology used herein is for the purpose of describing the particular embodiments only and is not intended to be limiting. As used herein, the singular form "a", "an" and "the" include plural references unless the context clearly dictates otherwise. As used herein, the term "and / or" includes any and all combinations of one or more of the associated listed terms. As used herein, the term "includes" means includes but not limited to, and the term "including" means including but not limited to.

[0173] The specific embodiments described herein are examples of the application and are not intended to limit the application. The application can be variously modified and altered, and can be carried out by different embodiments without departing from the scope of the application. Therefore, the scope of the application is not intended to be limited to the embodiments described herein but is to be accorded the full scope consistent with the language of the claims, wherein reference to an alternative embodiment incorporates the essential characteristics of that embodiment.

Claims

1. A fluid machine characterized by, The fluid machine comprises: a crankshaft (10) provided with two eccentric portions (11) along the axial direction thereof; a cylinder sleeve (20) eccentrically arranged with the crankshaft (10) and having a fixed eccentric distance; a cross groove structure (30) rotatably arranged in the cylinder sleeve (20), the cross groove structure (30) having two limiting channels (31) sequentially arranged along the axial direction of the crankshaft (10), the extending direction of the limiting channels (31) being perpendicular to the axial direction of the crankshaft (10); two sliders (40) each having a through hole (41), the two eccentric portions (11) corresponding to extending into the two through holes (41) of the two sliders (40), the two sliders (40) corresponding to being slidingly arranged in the two limiting channels (31) and forming a variable volume cavity (311) in the sliding direction of the sliders (40), the crankshaft (10) rotating to drive the sliders (40) to reciprocatingly slide in the limiting channels (31) while interacting with the cross groove structure (30), so that the cross groove structure (30) and the sliders (40) rotate in the cylinder sleeve (20); two flanges (50) respectively arranged at the two axial ends of the cylinder sleeve (20), at least one of the two flanges (50) being provided with an exhaust passage (51); wherein the side wall of the cylinder sleeve (20) is provided with two exhaust ports (22) arranged at intervals along the axial direction of the cylinder sleeve (20), and the two exhaust ports (22) are both in communication with the exhaust passage (51); the cross-sectional area of the hole section of the exhaust port (22) is S1, and the volume of a single variable volume cavity (311) is V1, wherein 750≦V1 / S1≦3300, and the value range of V1 / S1 is the ratio when V1 is at the maximum value.

2. The fluid machine of claim 1, wherein, The positions of the two exhaust ports (22) in the circumferential direction of the cylinder sleeve (20) are consistent.

3. The fluid machine according to claim 1, wherein the projection of the slider (40) in the axial direction of the through hole (41) has two opposite parallel straight line segments and an arc segment connecting the end portions of the two straight line segments; the arrangement position of the exhaust port (22) in the circumferential direction of the cylinder sleeve (20) is within the angle range of (arccos(2R / B)~2×arccos(2R / B)), wherein R is the inner circle radius of the cylinder sleeve (20), and B is the distance between the two opposite parallel straight line segments of the projection of the slider (40) in the axial direction of the through hole (41).

4. The fluid machine of claim 1, wherein, An exhaust cavity (25) is formed in the outer wall of the cylinder sleeve (20), and the exhaust port (22) is communicated to the exhaust cavity (25) through the inner wall of the cylinder sleeve (20).

5. The fluid machine of claim 4, wherein, A communication hole (26) is further arranged on the axial end surface of the cylinder sleeve (20), and the communication hole (26) is communicated with the exhaust cavity (25) and the exhaust passage (51).

6. The fluid machine of claim 4, wherein, The exhaust cavity (25) is two, and the two exhaust cavities (25) are arranged in the axial direction of the cylinder sleeve (20) and are communicated with the two exhaust ports (22) one by one.

7. The fluid machine of claim 6, wherein, The two exhaust cavities (25) are communicated through an exhaust communication hole (28) extending in the axial direction of the cylinder sleeve (20).

8. The fluid machine of claim 4, wherein, The distance between the plane where the end of the exhaust port (22) communicated with the exhaust cavity (25) is located and the axis of the cylinder sleeve (20) is K, and the inner radius of the cylinder sleeve (20) is R, wherein 1mm≦K-R≦5mm.

9. The fluid machine of claim 4, wherein, The cavity sectional area of the exhaust cavity (25) in the axial direction of the cylinder sleeve (20) is S2, the height of a single exhaust cavity (25) in the axial direction of the cylinder sleeve (20) is M, and the displacement of the fluid machine is V, wherein 0.5≦(M×S2) / V≦5.

10. The fluid machine of claim 1, wherein, An exhaust cavity (25) is formed in the outer wall of the cylinder sleeve (20), and a boss structure (29) is arranged on the cavity wall surface of the exhaust cavity (25), and the exhaust port (22) is communicated to the boss structure (29) through the inner wall of the cylinder sleeve (20) and communicated with the exhaust cavity (25).

11. The fluid machine of claim 10, wherein, The thickness of the boss structure (29) in the extension direction of the exhaust port (22) is N, wherein 0.05mm≦N≦3mm.

12. The fluid machine of claim 4 or 10, wherein, The exhaust cavity (25) penetrates the outer wall surface of the cylinder sleeve (20), and the fluid machine further comprises an exhaust cover plate connected with the cylinder sleeve (20) and sealing the exhaust cavity (25).

13. The fluid machine of any one of claims 1 to 11, wherein, The phase difference between the two eccentric parts (11) has a first included angle A, the eccentric amount of the two eccentric parts (11) is equal, and the extension direction of the two limiting channels (31) has a second included angle B, wherein the first included angle A is twice the second included angle B.

14. A heat exchange apparatus comprising a fluid machine, characterized by The fluid machine is the fluid machine of any one of claims 1 to 13. The fluid machine is the fluid machine of any one of claims 1 to 13.

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