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. The two sliding blocks are correspondingly arranged in the two limiting channels and form a variable volume cavity. At least one of the two flanges has an air inlet channel. The air inlet channel comprises a radial air suction hole and an axial air suction hole which are sequentially connected. The ratio S / V of the sectional area S of the hole section of the radial air suction hole to the displacement V of the fluid machine ranges from 0.006 to 0.01. The application solves the problems of low energy efficiency, large noise and insufficient air suction 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 compressor has the phenomenon of insufficient suction, which leads to an increase in suction loss. 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 and large noise of the compressor in the prior art and how to solve the problem of insufficient suction of the compressor.

[0006] In order to achieve the above-mentioned purpose, according to one aspect of the present application, a fluid machine is provided, which comprises a crankshaft, a cylinder sleeve, a cross groove structure, a sliding block and two flanges, the crankshaft is provided with two eccentric parts along its axial direction; 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 axial ends of the cylinder sleeve respectively, at least one of the two flanges has an air inlet channel, the air inlet channel is used for communicating with the variable volume chamber, and the air inlet channel comprises a radial air inlet hole and an axial air inlet hole which are sequentially communicated, wherein the ratio S / V of the cross-sectional area S of the hole cross-section of the radial air inlet hole to the displacement V of the fluid machine ranges from 0.006 to 0.01.

[0007] Further, the inner wall surface of the cylinder sleeve has an air suction cavity, and the air inlet channel communicates with the variable volume chamber through the air suction cavity.

[0008] Further, the suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve by a first preset distance to form an arc-shaped suction cavity.

[0009] Further, the suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve by a first preset distance to form an arc-shaped suction cavity.

[0010] Further, the suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve by a first preset distance to form an arc-shaped suction cavity.

[0011] Further, the suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve by a first preset distance to form an arc-shaped suction cavity.

[0012] Further, the suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve by a first preset distance to form an arc-shaped suction cavity.

[0013] Further, the suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve by a first preset distance to form an arc-shaped suction cavity.

[0014] Further, the suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve by a first preset distance to form an arc-shaped suction cavity.

[0015] Further, the suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve by a first preset distance to form an arc-shaped suction cavity.

[0016] Further, the suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve by a first preset distance to form an arc-shaped suction cavity.

[0017] Further, the fluid machine is a compressor.

[0018] Further, the suction cavity extends along the circumferential direction of the inner wall surface of the cylinder sleeve by a first preset distance to form an arc-shaped suction cavity.

[0019] Further, the fluid machine is an expander.

[0020] Further, the outer wall of the cylinder sleeve is provided with an exhaust cavity, the cylinder sleeve is further provided with an exhaust port, 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.

[0021] Further, the exhaust port is two, the two exhaust ports are arranged in the axial direction of the cylinder sleeve, and the exhaust valve assembly is two groups, and the two groups of exhaust valve assemblies are arranged corresponding to the two exhaust ports.

[0022] Further, the exhaust cavity is one, and the at least one axial end surface of the cylinder sleeve is further provided with a communication hole, the communication hole is communicated with the exhaust cavity, and the exhaust passage is arranged on the flange opposite to the communication hole among the two flanges, and the communication hole is communicated with the exhaust passage.

[0023] Further, the exhaust port is two, the two exhaust ports are arranged in the axial direction of the cylinder sleeve, and the exhaust valve assembly is two groups, and the two groups of exhaust valve assemblies are arranged corresponding to the two exhaust ports.

[0024] Further, the two exhaust cavities are communicated through the exhaust communication port, the at least one axial end surface of the cylinder sleeve is further provided with a communication hole, the communication hole is communicated with the exhaust cavity, and the exhaust passage is arranged on the flange opposite to the communication hole among the two flanges, and the communication hole is communicated with the exhaust passage.

[0025] Further, the two exhaust cavities are not communicated, the two axial end surfaces of the cylinder sleeve are both provided with a communication hole, the two communication holes are respectively communicated with the two exhaust cavities, the exhaust passage is arranged on the position opposite to the communication hole among the two flanges, and the communication hole is communicated with the exhaust passage.

[0026] Further, the exhaust port is one, and the exhaust port is communicated with the variable volume cavity on the corresponding side, the at least one axial end surface of the cylinder sleeve is further provided with a communication hole, the communication hole is communicated with the exhaust cavity, the first exhaust passage is arranged on the flange opposite to the communication hole among the two flanges, and the communication hole is communicated with the first exhaust passage; the flange away from the exhaust port on one side of the two flanges has a second exhaust passage, and the second exhaust passage is communicated with the variable volume cavity on the corresponding side.

[0027] 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.

[0028] Further, the end of the intake passage is a compressed intake port, the exhaust port on the cylinder sleeve is a compressed exhaust port, when any slider is in the intake position, the compressed intake port is communicated with the variable volume cavity on the corresponding side; when any slider is in the exhaust position, the variable volume cavity on the corresponding side is communicated with the compressed exhaust port.

[0029] Further, the fluid machine is a compressor.

[0030] Further, the end of the intake passage is an expansion exhaust port, and the exhaust port on the cylinder sleeve is an expansion intake port, when any one of the sliders is in the intake position, the expansion exhaust port is communicated with the variable volume chamber on the corresponding side; when any one of the sliders is in the exhaust position, the variable volume chamber on the corresponding side is communicated with the expansion intake port.

[0031] Further, the fluid machine is an expander.

[0032] Further, the phase difference between the two eccentric portions has 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 second included angle B, wherein the first included angle A is twice the second included angle B.

[0033] According to another aspect of the present application, a heat exchange device is provided, comprising the fluid machine.

[0034] According to the technical scheme of the present application, the intake passage on the flange is arranged in a structure form comprising a radial suction hole and an axial suction hole communicated in sequence, and meanwhile, the ratio S / V of the cross-sectional area S of the radial suction hole to the displacement V of the fluid machine is reasonably optimized to be within the range of 0.006-0.01, so that the suction loss of the fluid machine caused by insufficient suction is avoided, and thus the volumetric efficiency of the fluid machine in this range can be optimized. BRIEF DESCRIPTION OF DRAWINGS

[0035] The drawings accompanying the specification of this application form a part thereof, serve to provide further understanding of the present application, and together with the description of the exemplary embodiments of the present application, serve to explain the present application, and do not constitute improper limitations on the present application. In the drawings:

[0036] Figure 1 An internal structure schematic diagram of the compressor according to the embodiment one of the present application is shown;

[0037] Figure 2 An exploded structure schematic diagram of the pump body assembly of the compressor in Figure 1 is shown;

[0038] Figure 3 An assembly structure schematic diagram of the crankshaft, cross groove structure and slider in Figure 2 is shown;

[0039] Figure 4 A sectional structure schematic diagram of the crankshaft, cross groove structure and slider in Figure 3 is shown;

[0040] Figure 5 A sectional structure schematic diagram of the crankshaft, cross groove structure and slider in Figure 2Structure diagram of the eccentricity of the shaft body portion and the two eccentric portions of the crankshaft in the crankshaft and cylinder liner assembly of the compressor in the present application;

[0041] Figure 6 Structure diagram of the assembly eccentricity of the crankshaft and cylinder liner in the compressor in the present application; Figure 2

[0042] Figure 7 Structure diagram of the eccentricity between the cylinder liner and the lower flange in the compressor in the present application; Figure 2

[0043] Figure 8 Structure diagram of the slider in the axial direction of the through hole in the compressor in the present application; Figure 2

[0044] Figure 9 Structure diagram of the upper flange suction of the pump body assembly of the compressor in the present application; Figure 1

[0045] Figure 10 Structure diagram of the suction path of the upper flange suction of the pump body assembly in the compressor in the present application; Figure 9

[0046] Figure 11 Structure diagram of the cross-sectional view of the C-C view in the compressor in the present application; Figure 9

[0047] Figure 12 Structure diagram of the cross-sectional view of the D-D view in the compressor in the present application; Figure 9

[0048] Figure 13 Structure diagram of the cylinder liner according to an optional embodiment of the present application;

[0049] Figure 14 Structure diagram of another view of the cylinder liner in the compressor in the present application; Figure 13

[0050] Figure 15 Structure diagram of the cross-sectional view of the F-F view in the compressor in the present application; Figure 14

[0051] Structure diagram of the upper flange according to an optional embodiment of the present application; Figure 16

[0052] Figure 17 Structure diagram of the bottom view of the upper flange in the compressor in the present application; Figure 16

[0053] Figure 18 Structure diagram of the internal structure of the compressor according to the second embodiment of the present application;

[0054] Figure 19 ​​​​​​​​​​A structural diagram of the lower flange suction of the pump body assembly of the compressor in Figure 18 ;

[0055] Figure 20 A structural diagram of the cylinder liner according to an alternative embodiment of the present application is shown;

[0056] Figure 21 A structural diagram of the bottom view of the cylinder liner in Figure 20 ;

[0057] Figure 22 A structural diagram of another view of the cylinder liner in Figure 21 ;

[0058] Figure 23 A structural diagram of the G-G view in Figure 22 ;

[0059] Figure 24 A structural diagram of the lower flange according to an alternative embodiment of the present application is shown;

[0060] Figure 25 A structural diagram of the bottom view of the lower flange in Figure 24 ;

[0061] Figure 26 A structural diagram of the internal structure of the compressor according to embodiment three of the present application is shown;

[0062] Figure 27 A structural diagram of the upper flange and lower flange suction of the pump body assembly of the compressor in Figure 26 ;

[0063] Figure 28 A structural diagram of the cylinder liner according to an alternative embodiment of the present application is shown;

[0064] Figure 29 A structural diagram of the bottom view of the cylinder liner in Figure 28 ;

[0065] Figure 30 A structural diagram of another view of the cylinder liner in Figure 28 ;

[0066] Figure 31 A sectional structural diagram of the H-H view in Figure 30 ;

[0067] Figure 32 A structural diagram of the exhaust of the pump body assembly according to an alternative embodiment of the present application is shown;

[0068] Figure 33 A structural diagram of the exhaust of the pump body assembly according to an alternative embodiment of the present application is shown;Figure 32 Structure diagram of the upper flange of the pump body assembly in

[0069] Figure 34 Structure diagram of the cylinder sleeve of the pump body assembly in Figure 32 Structure diagram of the cylinder sleeve of the pump body assembly in

[0070] Figure 35 Structure diagram of the exhaust of the pump body assembly according to another alternative embodiment of the present application

[0071] Figure 36 Structure diagram of the upper flange of the pump body assembly in Figure 35 Structure diagram of the upper flange of the pump body assembly in

[0072] Figure 37 Structure diagram of the cylinder sleeve of the pump body assembly in Figure 35 Structure diagram of the cylinder sleeve of the pump body assembly in

[0073] Figure 38 Mechanism principle diagram of the compressor operation according to an alternative embodiment of the present application

[0074] Figure 39 Mechanism principle diagram of the compressor operation in Figure 38 Mechanism principle diagram of the compressor operation in

[0075] Figure 40 Mechanism principle diagram of the compressor operation in the prior art

[0076] Figure 41 Mechanism principle diagram of the improved compressor operation in the prior art

[0077] Figure 42 Mechanism principle diagram of the compressor operation in Figure 41 Mechanism principle diagram of the compressor operation in

[0078] Figure 43 Mechanism principle diagram of the compressor operation in Figure 41 Mechanism principle diagram of the compressor operation in

[0079] Figure 44 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 compressor.

[0080] Among the above drawings, the following reference signs are included:

[0081] 10, crankshaft; 11, eccentric part; 12, shaft body portion

[0082] 20, cylinder liner; 22, exhaust port; 23, suction chamber; 24, suction communication chamber; 25, exhaust chamber; 26, communication hole; 27, bevel cut; 28, exhaust communication port;

[0083] 30, cross groove structure; 31, limiting channel; 311, variable volume chamber; 32, center hole;

[0084] 40, slider; 41, through hole; 42, extrusion surface;

[0085] 50, flange; 51, exhaust passage; 511, first exhaust passage; 512, second exhaust passage; 52, upper flange; 53, lower flange; 54, intake passage; 541, radial suction hole; 542, axial suction hole;

[0086] 70, exhaust cover plate;

[0087] 80, distributor component; 81, housing assembly; 82, motor assembly; 83, pump body assembly; 84, upper cover assembly; 85, lower cover assembly;

[0088] 90, fastener. DETAILED DESCRIPTION

[0089] 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 of the present application. 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 work fall within the scope of protection of the present application.

[0090] In the prior art, as shown in Figure 40 , 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.

[0091] 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.

[0092] 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 41As 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.

[0093] 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 the specific 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.

[0094] However, as shown in the prior art, Figure 42 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 O1O0 and the sliding direction of the slider in the limiting groove.

[0095] As shown in the prior art, Figure 43 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.

[0096] Based on this, the application proposes a brand new mechanism principle with a cross groove structure with two limiting channels and double sliders, and a brand 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.

[0097] 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 and a heat exchange equipment, wherein the heat exchange equipment comprises the above and the following fluid machine.

[0098] The fluid machine in the application comprises a crankshaft 10, a cylinder sleeve 20, a cross groove structure 30 and a sliding block 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 sliding block 40 has a through hole 41, and there are two sliding blocks 40, the two eccentric parts 11 correspondingly extend into the two through holes 41 of the two sliding blocks 40, and the two sliding blocks 40 are correspondingly 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 sliding block 40, and when the crankshaft 10 rotates to drive the sliding block 40 to reciprocally slide in the limiting channel 31, the cross groove structure 30 and the sliding block 40 rotate in the cylinder sleeve 20.

[0099] By arranging the cross groove structure 30 in the form of two limiting channels 31 and correspondingly arranging two sliding blocks 40, the two eccentric parts 11 of the crankshaft correspondingly extend into the two through holes 41 of the two sliding blocks 40, and at the same time, the two sliding blocks 40 are correspondingly 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 twice the second included angle B between the extension directions of the two limiting channels 31, when one of the two sliding blocks 40 is at the dead center position, the driving torque of the eccentric part 11 corresponding to the sliding block 40 at the dead center position is 0, and the sliding block 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 sliding block 40 is the maximum value, which ensures that the eccentric part 11 with the maximum driving torque can normally drive the corresponding sliding block 40 to rotate, thereby driving the cross groove structure 30 to rotate through the sliding block 40, and further driving the sliding block 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 movement mechanism, and improving the movement reliability of the fluid machine, thereby ensuring the working reliability of the heat exchange equipment.

[0100] 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, thereby ensuring the working reliability of the heat exchange equipment.

[0101] It should be noted that in the application, the first included angle A and the second included angle B are not zero.

[0102] As Figure 38and Figure 39 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.

[0103] 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 38 ).

[0104] like Figure 38 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.

[0105] like Figure 39 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.

[0106] 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.

[0107] 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, 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 slider 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, improve the movement reliability of the fluid machine, and thus ensure the working reliability of the heat exchange equipment.

[0108] It should be noted that, in the present application, the maximum force arm of the driving torque of the eccentric part 11 is 2e.

[0109] 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.

[0110] It should be noted that, in the present application, in the process of rotating the crankshaft 10, the crankshaft 10 rotates 2 circles, and completes 4 times of suction and exhaust processes.

[0111] 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.

[0112] As Figures 1 to 37As shown, the fluid machine further comprises a flange 50 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 between the crankshaft 10 and the cross groove structure 30 is determined by the relative position relationship between the flange 50 and the cylinder sleeve 20, wherein the flange 50 is fixed on the cylinder sleeve 20 through fasteners 90, the relative position between 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 between the axis of the crankshaft 10 and the axis of the cross groove structure 30 is determined by the relative position between the axis of the flange 50 and the axis of the inner ring of the cylinder sleeve 20. The essence of centering the flange 50 is to make the eccentricity of the eccentric part 11 equal to the assembly eccentricity between the crankshaft 10 and the cylinder sleeve 20.

[0113] Specifically, as shown in the drawings, Figure 5 the eccentricities of the two eccentric parts 11 are both equal to e, as shown in the drawings, Figure 6 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), the flange 50 comprises an upper flange 52 and a lower flange 53, as shown in the drawings, Figure 7 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, i.e., equal to the eccentricity of the eccentric part 11.

[0114] Optionally, the first assembly gap between the crankshaft 10 and the flange 50 is 0.005mm-0.05mm.

[0115] Preferably, the first assembly gap is 0.01-0.03mm.

[0116] 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.

[0117] 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.

[0118] As shown in the drawings, Figures 1 to 6 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.

[0119] 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.

[0120] Optionally, the first segment and the second segment are detachably connected. In this way, the assembly and disassembly of the crankshaft 10 are facilitated.

[0121] As shown in Figures 1 to 6 , 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.

[0122] 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.

[0123] As shown in Figure 2 and Figure 3 , 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.

[0124] 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.

[0125] Preferably, the first included angle A is 160 degrees, and the second included angle B is 80 degrees.

[0126] Preferably, the first included angle A is 165 degrees, and the second included angle B is 82.5 degrees.

[0127] Preferably, the first included angle A is 170 degrees, and the second included angle B is 85 degrees.

[0128] Preferably, the first included angle A is 175 degrees, and the second included angle B is 87.5 degrees.

[0129] Preferably, the first included angle A is 180 degrees, and the second included angle B is 90 degrees.

[0130] Preferably, the first included angle A is 185 degrees, and the second included angle B is 92.5 degrees.

[0131] Preferably, the first included angle A is 190 degrees, and the second included angle B is 95 degrees.

[0132] Preferably, the first included angle A is 195 degrees, and the second included angle B is 97.5 degrees.

[0133] 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.

[0134] As shown in Figures 1 to 6 , the eccentric portion 11 is cylindrical.

[0135] 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.

[0136] Optionally, the proximal end of the eccentric portion 11 protrudes from the outer circle of the shaft body portion 12 of the crankshaft 10.

[0137] 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.

[0138] It should be noted that in an embodiment of the present application not shown in the figure, the slider 40 comprises a plurality of substructures, which are spliced to form a through hole 41.

[0139] As shown in Figures 1 to 6 , 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.

[0140] As shown in Figure 2 , 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.

[0141] 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.

[0142] As shown in Figure 8 , 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.

[0143] 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 8 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 8 The dashed X-line in the diagram represents the circle containing the center of the two arc surfaces.

[0144] Optionally, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20.

[0145] 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.

[0146] Preferably, the difference ranges from -0.02 to 0.02 mm.

[0147] 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.

[0148] Preferably, S 滑块 / S 排 The value is 12 to 18.

[0149] 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.

[0150] Alternatively, the above-mentioned components can be connected by welding, heat fitting, or cold pressing.

[0151] 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, and then 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 details can be seen from Figure 2 and Figure 3 .

[0152] 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, and for the compressor, the crankshaft 10 rotates twice, and a total of four suction and exhaust processes are completed.

[0153] 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.

[0154] The operation of the compressor will be specifically introduced as follows:

[0155] As shown in Figure 1 , the motor assembly 82 drives the crankshaft 10 to rotate, the two eccentric parts 11 of the crankshaft 10 respectively drive the corresponding two sliders 40 to move, the slider 40 revolves around the axis of the crankshaft 10 while the slider 40 rotates relative to the eccentric part 11, and the slider 40 reciprocates along the limiting channel 31 and drives the cross groove structure 30 to rotate in the cylinder sleeve 20, and the slider 40 revolves while reciprocating along the limiting channel 31 to form a cross slider mechanism movement mode.

[0156] In order to solve the problem of insufficient suction of the compressor, the present application supplements the following contents on the basis of the above fluid machine, and the details are as follows:

[0157] Embodiment one

[0158] As shown in Figures 9 to 17 , Figure 44As shown, the fluid machine further comprises two flanges 50, the two flanges 50 are respectively arranged at the axial two ends of the cylinder sleeve 20, at least one of the two flanges 50 is provided with an intake passage 54, the intake passage 54 is used for communicating with the variable volume chamber 311, the intake passage 54 comprises a radial suction hole 541 and an axial suction hole 542 which are communicated in sequence, wherein the ratio S / V of the cross-sectional area S of the hole section of the radial suction hole 541 to the displacement V of the fluid machine ranges from 0.006 to 0.01.

[0159] By setting the intake passage 54 on the flange 50 to have a structure comprising a radial suction hole 541 and an axial suction hole 542 which are communicated in sequence, and at the same time, reasonably optimizing the ratio S / V of the cross-sectional area S of the hole section of the radial suction hole 541 to the displacement V of the fluid machine within the range of 0.006 to 0.01, the loss of suction caused by insufficient suction of the compressor is avoided, thereby ensuring that the volumetric efficiency of the compressor can reach the optimum within this range.

[0160] As shown, Figures 9 to 17 The inner wall surface of the cylinder sleeve 20 has a suction chamber 23, and the intake passage 54 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 fully suck in, thereby enabling the compressor to fully suck in, and when the suction is insufficient, the stored gas can be supplied to the variable volume chamber 311 in time to ensure the compression efficiency of the compressor.

[0161] Optionally, the suction chamber 23 is a cavity formed by hollowing out the inner wall surface of the cylinder sleeve 20 in the radial direction, and the suction chamber 23 can be one or two.

[0162] Specifically, the suction chamber 23 extends a first predetermined distance around the circumference of the inner wall surface of the cylinder sleeve 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.

[0163] As shown, Figures 9 to 17 The two suction chambers 23 are spaced apart along the axial direction of the cylinder sleeve 20, when one of the two flanges 50 has an intake passage 54, the cylinder sleeve 20 further has a suction communication chamber 24, both of the two suction chambers 23 communicate with the suction communication chamber 24, and the intake passage 54 communicates with the suction chamber 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.

[0164] As shown, Figures 9 to 17 The suction communication chamber 24 extends a second predetermined distance along the axial direction of the cylinder sleeve 20, and the one end of the suction communication chamber 24 towards the flange 50 with the intake passage 54 penetrates through the axial end surface of the cylinder sleeve 20. In this way, it is convenient to open the suction communication chamber 24 from the end surface of the cylinder sleeve 20, and ensures the processing convenience of the suction communication chamber 24.

[0165] It should be noted that in the present embodiment, the upper flange 52 of the two flanges 50 has the air inlet passage 54.

[0166] Embodiment Two

[0167] It should be noted that the difference between the present embodiment and Embodiment One is that, as shown in Figures 18 to 25 the lower flange 53 of the two flanges 50 has the air inlet passage 54.

[0168] Embodiment Three

[0169] As shown in Figures 26 to 31 the air suction cavities 23 are two, the two air suction cavities 23 are arranged at intervals along the axial direction of the cylinder sleeve 20, when the two flanges 50 both have the air inlet passages 54, the cylinder sleeve 20 further has two air suction communication cavities 24, the two air suction cavities 23 are both communicated with the air suction communication cavity 24, and the two air inlet passages 54 are both communicated with the corresponding air suction cavity 23 through the corresponding air suction communication cavity 24. In this way, the purpose of independent air suction of the upper flange 52 and the lower flange 53 is achieved.

[0170] Further, the air suction communication cavity 24 extends along the axial direction of the cylinder sleeve 20 by a third preset distance, and one end of the air suction communication cavity 24 towards the corresponding flange 50 penetrates the axial end surface of the cylinder sleeve 20. In this way, the air suction communication cavity 24 is conveniently opened from the end surface of the cylinder sleeve 20, and the machining convenience of the air suction communication cavity 24 is ensured.

[0171] It should be noted that in an embodiment of the present application not shown in the figure, the air suction cavities 23 are two, the two air suction cavities 23 are arranged at intervals along the axial direction of the cylinder sleeve 20, when the two flanges 50 both have the air inlet passages 54, the cylinder sleeve 20 further has the air suction communication cavity 24, the two air suction cavities 23 are both communicated with the air suction communication cavity 24, and the air inlet passage 54 is communicated with the air suction cavity 23 through the air suction communication cavity 24.

[0172] Further, the air suction communication cavity 24 extends along the axial direction of the cylinder sleeve 20 by a fourth preset distance, and both ends of the air suction communication cavity 24 penetrate the two axial end surfaces of the cylinder sleeve 20. In this way, the air suction communication cavity 24 is conveniently opened from the end surface of the cylinder sleeve 20, and the machining convenience of the air suction communication cavity 24 is ensured.

[0173] Embodiment One of Exhaust, the upper flange 52 and the lower flange 53 are respectively exhausted, and the specific implementation is as follows:

[0174] It should be noted that in an embodiment of the application not shown in the drawings, the end surface of the two flanges 50 is provided with an exhaust passage 51, and the two exhaust passages 51 are respectively communicated with the variable volume chamber 311 on the corresponding side. In this way, the exhaust passage 51 is arranged on the upper flange 52 and the lower flange 53, respectively, instead of being arranged on the arc surface of the cylinder sleeve 20, thereby reducing the manufacturing difficulty of the exhaust passage 51.

[0175] Specifically, the end of the intake passage 54 is a compressed intake port, and the initial end of the exhaust passage 51 is a compressed exhaust port. When any one of the sliders 40 is in the intake position, the compressed intake port is communicated with the variable volume chamber 311 on the corresponding side. When any one of the sliders 40 is in the exhaust position, the variable volume chamber 311 on the corresponding side is communicated with the compressed exhaust port. In this way, when the high-pressure gas enters the variable volume chamber 311 through the compressed intake port, the high-pressure gas drives the cross groove structure 30 to rotate, the cross groove structure 30 rotates to drive the slider 40 to rotate, and at the same time, the slider 40 linearly slides relative to the cross groove structure 30, thereby driving the eccentric part 11 to rotate, i.e., driving the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can output work.

[0176] Other use occasions: the compressor can be used as an expander by exchanging the positions of the compressed intake port and the compressed exhaust port. That is, the compressed exhaust port is used as the suction port of the expander, high-pressure gas is introduced, other driving mechanisms rotate, and the gas is discharged through the compressed intake port (expander exhaust port) after expansion.

[0177] Specifically, the end of the intake passage 54 is a compressed intake port, and the initial end of the exhaust passage 51 is a compressed exhaust port. When any one of the sliders 40 is in the intake position, the compressed intake port is communicated with the variable volume chamber 311 on the corresponding side. When any one of the sliders 40 is in the exhaust position, the variable volume chamber 311 on the corresponding side is communicated with the compressed exhaust port. In this way, when the high-pressure gas enters the variable volume chamber 311 through the compressed intake port, the high-pressure gas drives the cross groove structure 30 to rotate, the cross groove structure 30 rotates to drive the slider 40 to rotate, and at the same time, the slider 40 linearly slides relative to the cross groove structure 30, thereby driving the eccentric part 11 to rotate, i.e., driving the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can output work.

[0178] Exhaust embodiment two, cylinder sleeve side exhaust, as follows:

[0179] As Figures 32 to 34As shown, the outer wall of the cylinder sleeve 20 is provided with an exhaust cavity 25, and the cylinder sleeve 20 is further provided with an exhaust port 22 which is communicated to the exhaust cavity 25 by the inner wall of the cylinder sleeve 20. The fluid machine further comprises an exhaust valve assembly which is arranged in the exhaust cavity 25 and corresponds to the exhaust port 22. 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, reasonably arranging the components, and improving the space utilization of the cylinder sleeve 20.

[0180] As shown, Figures 32 to 34 the exhaust port 22 is two, and the two exhaust ports 22 are arranged along the axial direction of the cylinder sleeve 20. The exhaust valve assembly is two groups, and the two groups of exhaust valve assemblies are arranged corresponding to the two exhaust ports 22. In this way, since the two compression exhaust ports 22 are respectively provided with two groups of exhaust valve assemblies, the leakage of the gas in the variable volume chamber 311 is effectively avoided, and the compression efficiency of the variable volume chamber 311 is ensured.

[0181] Further, the exhaust valve assembly is connected with the cylinder sleeve 20 through a fastener, and the exhaust valve assembly comprises an exhaust valve plate and a valve plate baffle. The exhaust valve plate is arranged in the exhaust cavity 25 and shields the corresponding compression exhaust port 22, and the valve plate baffle is arranged on the exhaust valve plate. In this way, the arrangement of the valve plate baffle effectively avoids the excessive opening of the exhaust valve plate, thereby ensuring the exhaust performance of the cylinder sleeve 20.

[0182] Optionally, the fastener is a screw.

[0183] In an embodiment of the present application which is not shown in the figure, the exhaust cavity 25 is one, and the at least one axial end surface of the cylinder sleeve 20 is further provided with a communication hole 26 which is communicated with the exhaust cavity 25. The flange 50 opposite to the communication hole 26 among the two flanges 50 is provided with an exhaust passage 51, and the communication hole 26 is communicated with the exhaust passage 51. In this way, the exhaust reliability of the cylinder sleeve 20 is ensured.

[0184] As shown, Figures 32 to 34 the exhaust port 22 is two, and the two exhaust ports 22 are arranged along the axial direction of the cylinder sleeve 20. The exhaust cavity 25 is two, and the two exhaust cavities 25 are arranged corresponding to the two exhaust ports 22 one by one. The exhaust valve assembly is two groups, and the two groups of exhaust valve assemblies are arranged corresponding to the two exhaust ports 22.

[0185] As shown, Figures 32 to 34 the two exhaust cavities 25 are communicated through an exhaust communication port 28, and the at least one axial end surface of the cylinder sleeve 20 is further provided with a communication hole 26 which is communicated with the exhaust cavity 25. The flange 50 opposite to the communication hole 26 among the two flanges 50 is provided with an exhaust passage 51, and the communication hole 26 is communicated with the exhaust passage 51. In this way, the exhaust of the cylinder sleeve 20 is performed through the exhaust passage 51 of the upper flange 52 after the exhaust.

[0186] In another embodiment of the application not shown in the drawings, the two exhaust cavities 25 are not communicated, and the two axial end faces of the cylinder sleeve 20 are each provided with a communication hole 26, the two communication holes 26 are respectively communicated with the two exhaust cavities 25, and the two flanges 50 are each provided with an exhaust passage 51 at a position opposite to the communication hole 26, and the communication hole 26 is communicated with the exhaust passage 51. In this way, the upper and lower parts of the cylinder sleeve 20 are respectively provided with side exhaust, and then the upper flange 52 is provided with upper exhaust, and the lower flange 53 is provided with lower exhaust.

[0187] In the third exhaust embodiment, the cylinder sleeve is provided with side exhaust and the flange is provided with end face exhaust, and the specific implementation is as follows:

[0188] As shown in Figures 35 to 37 , the exhaust port 22 is one, and the exhaust port 22 is communicated with the corresponding variable volume chamber 311, and at least one axial end face of the cylinder sleeve 20 is further provided with a communication hole 26, the communication hole 26 is communicated with the exhaust cavity 25, and the flange 50 opposite to the communication hole 26 is provided with a first exhaust passage 511, and the communication hole 26 is communicated with the first exhaust passage 511; the flange 50 away from the exhaust port 22 side of the two flanges 50 has a second exhaust passage 512, and the second exhaust passage 512 is communicated with the corresponding variable volume chamber 311. In this way, the side exhaust of the cylinder sleeve 20 is realized, and the end exhaust of the flange 50 is combined.

[0189] As shown in Figures 35 to 37 , the exhaust cavity 25 penetrates to the outer wall surface of the cylinder sleeve 20, and the fluid machine further comprises an exhaust cover plate 70, the exhaust cover plate 70 is connected with the cylinder sleeve 20 and seals the exhaust cavity 25. In this way, the exhaust cover plate 70 plays a role in separating the variable volume chamber 311 from the external space of the pump body assembly 83.

[0190] As shown in Figure 37 , the end inner circle of the cylinder sleeve 20 away from the exhaust port 22 side is provided with a bevel cut 27, and the bevel cut 27 is communicated with the second exhaust passage 512.

[0191] Specifically, the end of the intake passage 54 is a compression intake port, and the exhaust port 22 on the cylinder sleeve 20 is a compression exhaust port, when any one of the sliding blocks 40 is in the intake position, the compression intake port is communicated with the corresponding variable volume chamber 311; when any one of the sliding blocks 40 is in the exhaust position, the corresponding variable volume chamber 311 is communicated with the compression exhaust port. In this way, when the high-pressure gas enters the variable volume chamber 311 through the compression intake port, the high-pressure gas pushes the cross groove structure 30 to rotate, the cross groove structure 30 rotates to drive the sliding block 40 to rotate, and at the same time makes the sliding block 40 slide linearly relative to the cross groove structure 30, and further makes the sliding block 40 drive the eccentric part 11 to rotate, that is, drive the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power consuming equipment, the crankshaft 10 can output work.

[0192] Other use occasions: the compressor exchanges the suction and exhaust ports, and can be used as an expander. That is, the compression exhaust port of the compressor is used as the suction port of the expander, high-pressure gas is introduced, other driving mechanisms rotate, and the gas is discharged after expansion through the compression intake port (expander exhaust port).

[0193] Specifically, the end of the intake passage 54 is the expansion exhaust port 22, the exhaust port 22 on the cylinder sleeve 20 is the expansion intake port, when any slider 40 is in the intake position, the expansion exhaust port 22 is in communication with the variable volume chamber 311 on the corresponding side; when any slider 40 is in the exhaust position, the variable volume chamber 311 on the corresponding side is in communication with the expansion intake port. In this way, after the high-pressure gas enters the variable volume chamber 311 through the expansion intake port, the high-pressure gas drives the cross groove structure 30 to rotate, the cross groove structure 30 rotates to drive the slider 40 to rotate, and at the same time, the slider 40 linearly slides relative to the cross groove structure 30, thereby driving the slider 40 to rotate, that is, driving the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can output work.

[0194] Optionally, the inner wall surface of the cylinder sleeve 20 has an expansion exhaust cavity, and the expansion exhaust cavity is in communication with the expansion exhaust port.

[0195] Further, the expansion exhaust cavity extends by a first preset distance around the circumference of the inner wall surface of the cylinder sleeve 20 to form an arc-shaped expansion exhaust cavity, and the expansion exhaust cavity extends from the expansion exhaust port to the side where the expansion intake port is located, and the extension direction of the expansion exhaust cavity is the same as the rotation direction of the cross groove structure 30.

[0196] Further, the expansion exhaust cavity is two, and the two expansion exhaust cavities are arranged in an axial direction of the cylinder sleeve 20, the cylinder sleeve 20 further has an expansion exhaust communication cavity, the two expansion exhaust cavities are in communication with the expansion exhaust communication cavity, and the expansion exhaust port is in communication with the expansion exhaust cavity through the expansion exhaust communication cavity.

[0197] Further, the expansion exhaust communication cavity extends by a second preset distance in the axial direction of the cylinder sleeve 20, and at least one end of the expansion exhaust communication cavity penetrates the axial end surface of the cylinder sleeve 20.

[0198] It should be noted that the terminology used herein is for the purpose of describing specific embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or groups thereof.

[0199] The foregoing is a summary and thus contains only the most basic embodiment of the application. The application can be practiced with modification and alteration and can take many different forms. Specific embodiments of the application have been chosen for purposes of illustration and example, but are understood not to limit the scope of the application, except insofar as they appear in the appended claims. The foregoing summary as well as the following detailed description are better understood when read in conjunction with the drawings, which are intended to illustrate and not to limit the application. As used herein, the term "or" as used herein, unless otherwise indicated, is intended to cover various combinations. For example, if a list is preceded by "at least one of... A or B" that list is intended to cover either A or B or A and B. Further, unless otherwise indicated, singular articles and / or single plural forms are to be construed as including their plural and / or plural -toreal counterparts.

[0200] For purposes of the US, the phrase "at least one of A or B" should be construed to include A alone, B alone, or A and B together. For purposes of the US, the terms "comprising", "including", and "having" and variations thereof herein, are intended to be open-ended terms. For purposes of the US, the terms "another" and "an" are defined as one or more unless explicitly stated otherwise.

[0201] 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 articles "a", "an" and "the" can be intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms "comprises", "comprising", "including", and "having" are is intended to be open-ended and allow for the possibility that there are other elements or steps. The terms "another" and "an" are defined as one or more unless explicitly stated otherwise.

[0202] 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 articles "a", "an" and "the" can be intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms "comprises", "comprising", "including", and "having" are is intended to be open-ended and allow for the possibility that there are other elements or steps. The terms "another" and "an" are defined as one or more unless explicitly stated otherwise.

[0203] The above merely provides the preferred embodiments of the present application, and is not used to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modifications, equivalent replacements, improvements, etc. made within the principles and technical scope of the present application shall fall into the scope of the present application.

Claims

1. A fluid machine characterized by, The application relates to a fluid machine, comprising: a crankshaft (10) provided with two eccentric portions (11) along the axial direction; a cylinder sleeve (20) eccentrically arranged with the crankshaft (10) and fixed with an eccentric distance; a cross groove structure (30) rotatably arranged in the cylinder sleeve (20), the cross groove structure (30) is provided with two limiting channels (31) sequentially arranged along the axial direction of the crankshaft (10), and the extending direction of the limiting channels (31) is perpendicular to the axial direction of the crankshaft (10); two sliders (40) provided with through holes (41), the two eccentric portions (11) correspondingly extend into the two through holes (41) of the two sliders (40), and the two sliders (40) are correspondingly arranged in the two limiting channels (31) and form a variable volume cavity (311) in the sliding direction of the sliders (40); when the crankshaft (10) rotates to drive the sliders (40) to reciprocally slide in the limiting channels (31) and interact with the cross groove structure (30), the cross groove structure (30) and the sliders (40) rotate in the cylinder sleeve (20); two flanges (50) arranged at the two axial ends of the cylinder sleeve (20) respectively, at least one of the two flanges (50) is provided with an air inlet channel (54) for communicating with the variable volume cavity (311), and the air inlet channel (54) comprises a radial air inlet hole (541) and an axial air inlet hole (542) sequentially communicated, wherein the ratio S / V of the sectional area S of the hole section of the radial air inlet hole (541) to the displacement V of the fluid machine ranges from 0.006 to 0.

01. The inner wall surface of the cylinder sleeve (20) is provided with an air suction cavity (23), and the air inlet channel (54) communicates with the variable volume cavity (311) through the air suction cavity (23). The air suction cavity (23) extends by a first preset distance along the circumference of the inner wall surface of the cylinder sleeve (20) to form an arc-shaped air suction cavity (23). The air suction cavity (23) is provided with two air suction cavities (23) arranged at intervals along the axial direction of the cylinder sleeve (20), when one of the two flanges (50) is provided with the air inlet channel (54), the cylinder sleeve (20) is further provided with an air communication cavity (24), the two air suction cavities (23) communicate with the air communication cavity (24), and the air inlet channel (54) communicates with the air suction cavities (23) through the air communication cavity (24). The air communication cavity (24) extends by a second preset distance along the axial direction of the cylinder sleeve (20), and the air communication cavity (24) penetrates through the axial end surface of the cylinder sleeve (20) towards one end of the flange (50) provided with the air inlet channel (54). ​ 2. The fluid machine of claim 1, wherein, ​ 3. The fluid machine of claim 2, wherein, ​ 4. The fluid machine of claim 2, wherein, ​ 5. The fluid machine of claim 4, wherein, ​ 6. The fluid machine of claim 2, wherein, The suction cavities (23) are two, and the two suction cavities (23) are arranged axially spaced apart along the cylinder sleeve (20). When the two flanges (50) are both provided with the intake passages (54), the cylinder sleeve (20) is further provided with two suction communication cavities (24), the two suction cavities (23) are communicated with the two suction communication cavities (24) respectively, and the two intake passages (54) are communicated with the corresponding suction cavities (23) through the corresponding suction communication cavities (24) respectively.

7. The fluid machine of claim 6, wherein, The suction communication cavity (24) extends along the axial direction of the cylinder sleeve (20) by a third preset distance, and one end of the suction communication cavity (24) towards the corresponding flange (50) penetrates the axial end surface of the cylinder sleeve (20).

8. The fluid machine of claim 2, wherein, The suction cavities (23) are two, and the two suction cavities (23) are arranged axially spaced apart along the cylinder sleeve (20). When the two flanges (50) are both provided with the intake passages (54), the cylinder sleeve (20) is further provided with a suction communication cavity (24), and the two suction cavities (23) are communicated with the suction communication cavity (24). The intake passage (54) is communicated with the suction cavity (23) through the suction communication cavity (24).

9. The fluid machine of claim 8, wherein, The suction communication cavity (24) extends along the axial direction of the cylinder sleeve (20) by a fourth preset distance, and both ends of the suction communication cavity (24) penetrate the two axial end surfaces of the cylinder sleeve (20) respectively.

10. The fluid machine of claim 1, wherein, The end surface of the two flanges (50) is provided with an exhaust passage (51), and the two exhaust passages (51) are communicated with the corresponding variable volume cavities (311) respectively.

11. The fluid machine of claim 10, wherein, The end of the intake passage (54) is a compressed intake port, and the initial end of the exhaust passage (51) is a compressed exhaust port, When any one of the sliding blocks (40) is in the intake position, the compressed intake port is communicated with the corresponding variable volume cavity (311); When any one of the sliding blocks (40) is in the exhaust position, the corresponding variable volume cavity (311) is communicated with the compressed exhaust port.

12. The fluid machine of claim 11, wherein, The fluid machine is a compressor.

13. The fluid machine of claim 10, wherein, The end of the intake passage (54) is an expansion exhaust port, and the initial end of the exhaust passage (51) is an expansion intake port, When any one of the sliding blocks (40) is in the intake position, the expansion exhaust port is communicated with the corresponding variable volume cavity (311); When any one of the sliding blocks (40) is in the exhaust position, the corresponding variable volume cavity (311) is communicated with the expansion intake port.

14. The fluid machine of claim 13, wherein, The fluid machine is an expander.

15. The fluid machine of claim 1, wherein, An exhaust cavity (25) is formed in the outer wall of the cylinder sleeve (20), and the cylinder sleeve (20) is further provided with an exhaust port (22). The exhaust port (22) is communicated to the exhaust cavity (25) by the inner wall of the cylinder sleeve (20), and the fluid machine further comprises an exhaust valve assembly arranged in the exhaust cavity (25) and corresponding to the exhaust port (22).

16. The fluid machine of claim 15, wherein, The exhaust port (22) is two, two said exhaust port (22) along the axial spacing of the cylinder sleeve (20) is set, the exhaust valve assembly is two groups, two said exhaust valve assembly is set respectively corresponding two said exhaust port (22).

17. The fluid machine of claim 16, wherein, The exhaust cavity (25) is one, and the at least one axial end surface of the cylinder sleeve (20) is further provided with a communication hole (26), the communication hole (26) is communicated with the exhaust cavity (25), and the flange (50) opposite to the communication hole (26) is provided with an exhaust passage (51), and the communication hole (26) is communicated with the exhaust passage (51).

18. The fluid machine of claim 15, wherein, The exhaust port (22) is two, two said exhaust port (22) along the axial spacing of the cylinder sleeve (20) is set, the exhaust cavity (25) is two, two said exhaust cavity (25) and two said exhaust port (22) one-to-one setting, the exhaust valve assembly is two groups, two said exhaust valve assembly is set respectively corresponding two said exhaust port (22).

19. The fluid machine of claim 18, wherein, Two said exhaust cavity (25) is communicated through exhaust communication port (28), the at least one axial end surface of the cylinder sleeve (20) is further provided with a communication hole (26), the communication hole (26) is communicated with the exhaust cavity (25), and the flange (50) opposite to the communication hole (26) is provided with an exhaust passage (51), and the communication hole (26) is communicated with the exhaust passage (51).

20. The fluid machine of claim 18, wherein, Two said exhaust cavity (25) is not communicated, the two axial end surfaces of the cylinder sleeve (20) are provided with a communication hole (26), two said communication hole (26) is respectively communicated with two said exhaust cavity (25), two said flange (50) and the position of the communication hole (26) opposite are provided with exhaust passage (51), the communication hole (26) is communicated with the exhaust passage (51).

21. The fluid machine of claim 15, wherein, The exhaust port (22) is one, and the exhaust port (22) is communicated with the variable volume cavity (311) on the corresponding side, and the at least one axial end surface of the cylinder sleeve (20) is further provided with a communication hole (26), the communication hole (26) is communicated with the exhaust cavity (25), and the flange (50) opposite to the communication hole (26) is provided with a first exhaust passage (511), and the communication hole (26) is communicated with the first exhaust passage (511); the flange (50) of two said flange (50) away from the side of the exhaust port (22) has a second exhaust passage (512), and the second exhaust passage (512) is communicated with the variable volume cavity (311) on the corresponding side.

22. The fluid machine of claim 15, wherein, The exhaust cavity (25) penetrates to the outer wall surface of the cylinder sleeve (20), and the fluid machine further comprises an exhaust cover plate (70), the exhaust cover plate (70) is connected with the cylinder sleeve (20) and seals the exhaust cavity (25).

23. The fluid machine of any one of claims 15 to 22, wherein, The end of the intake passage (54) is a compressed intake port, and the exhaust port (22) on the cylinder sleeve (20) is a compressed exhaust port, When any one of the sliders (40) is in the intake position, the compression intake port is communicated with the variable volume chamber (311) of the corresponding side; When any one of the sliders (40) is in the exhaust position, the variable volume chamber (311) of the corresponding side is communicated with the compression exhaust port.

24. The fluid machine of claim 23, wherein, The fluid machine is a compressor.

25. The fluid machine of any one of claims 15 to 22, wherein, The end of the intake passage (54) is an expansion exhaust port (22), the exhaust port (22) on the cylinder sleeve (20) is an expansion intake port, When any one of the sliders (40) is in the intake position, the expansion exhaust port (22) is communicated with the variable volume chamber (311) of the corresponding side; When any one of the sliders (40) is in the exhaust position, the variable volume chamber (311) of the corresponding side is communicated with the expansion intake port.

26. The fluid machine of claim 25, wherein, The fluid machine is an expander.

27. The fluid machine of claim 1, wherein, The two eccentric parts (11) have a phase difference of a first included angle A, the eccentricity of the two eccentric parts (11) is equal, and the extension directions of the two limit 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.

28. A heat exchange apparatus comprising a fluid machine, characterized by The fluid machine is the fluid machine according to any one of claims 1 to 27.

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