Fluid machine and heat exchange device

Abstract

The application provides a fluid machine and heat exchange equipment, 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, the first radial gap between the outer circumferential surface of the cross groove structure and the inner wall surface of the cylinder sleeve ranges from 0.005mm to 0.1mm, the difference between the height H3 of the cylinder sleeve and the height H2 of the cross groove structure ranges from 0.008mm to 0.05mm, two limiting channels of the cross groove structure are sequentially arranged along the axial direction of the crankshaft, the extending direction of the limiting channels 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; and the two flanges are arranged at the two axial ends of the cylinder sleeve. The application solves the problems of low energy efficiency, large noise of the compressor in the prior art, and how to prevent the gap leakage and wear of the pump body assembly.

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, expanders and the like. 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 structure and principle, the optimization space is limited. Therefore, it is urgent to propose a compressor with high energy efficiency, low noise and the like.

[0004] In addition, considering that the assembly gap between each part in the pump body assembly of the compressor is not reasonably set, wear and gap leakage occur between the mutually contacting parts. 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 prevent the gap leakage and wear of the pump body assembly.

[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, wherein 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 and coaxially arranged with the cylinder sleeve, and the outer peripheral surface of the cross groove structure and the inner wall surface of the cylinder sleeve have a first radial gap, the range of the first radial gap is 0.005mm-0.1mm, the height H3 of the cylinder sleeve and the height H2 of the cross groove structure have a difference, the range of the difference is 0.008mm-0.05mm, the cross groove structure has two limiting channels, the two limiting channels are sequentially arranged along the axial direction of the crankshaft, and the extending 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 cavity, the variable volume cavity is located in the sliding direction of the sliding block, and the crankshaft rotates to drive the sliding block to reciprocatingly 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 two ends of the cylinder sleeve.

[0007] Further, the range of the first radial gap is 0.01-0.06mm.

[0008] Further, the difference value is in the range of 0.01mm-0.03mm.

[0009] Further, the projection of the sliding block in the sliding direction thereof is square; and the cross section of the limiting channel in the sliding direction of the sliding block is square.

[0010] Further, the difference value between the width B1 of the limiting channel and the width B2 of the sliding block is B1-B2, wherein the range of B1-B2 is 0.005mm-0.05mm.

[0011] Further, the range of B1-B2 is 0.01mm-0.02mm.

[0012] Further, the difference value between the height H of the sliding block and the depth H1 of the limiting channel is H-H1, wherein the range of H-H1 is 0mm-0.05mm.

[0013] Further, the range of H-H1 is 0.01mm-0.02mm.

[0014] Further, the ratio of the depth H1 of the limiting channel to the width B1 of the limiting channel is H1 / B1, wherein the range of H1 / B1 is 0.3-1.2.

[0015] Further, the ratio of the eccentricity e of the eccentric part to the outer radius D / 2 of the cross groove structure is e / D / 2, wherein the range of e / D / 2 is 0.02-0.06.

[0016] Further, the ratio of the height H2 of the cross groove structure to the outer diameter D of the cross groove structure is H2 / D, wherein the range of H2 / D is 0.4-2.

[0017] Further, the sealing distance F between the two limiting channels of the cross groove structure is in the range of 1mm-15mm.

[0018] Further, the phase difference between the two eccentric parts has a first included angle A, the eccentricities of the two eccentric parts are equal, and the phase difference between the extension directions of the two limiting channels has 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, wherein the fluid machine is the above-mentioned fluid machine.

[0020] The application optimizes the range of the first radial gap between the outer circumferential surface of the cross groove structure and the inner wall surface of the cylinder sleeve, so that the power consumption of the fluid machine can reach the optimal value; in addition, by optimizing the range of the difference between the height H3 of the cylinder sleeve and the height H2 of the cross groove structure, the gap fit between the end surface of the axial two ends of the cross groove structure and the end surface of the axial two ends of the cylinder sleeve is ensured, and the gap fit between the end surface of the axial two ends of the cross groove structure and the surface of the two flanges on the side of the cylinder sleeve is ensured, so that the cross groove structure is prevented from being stuck and worn during rotation, which is beneficial to reduce the power consumption of the fluid machine, while ensuring the sealing performance and refrigerating capacity of the fluid machine. BRIEF DESCRIPTION OF DRAWINGS

[0021] The drawings accompanying the specification of this application form a part thereof, serve to provide further understanding of the application, and together with the description of the application, serve to explain the application. In the drawings:

[0022] Figure 1 An internal structure schematic diagram of a compressor according to an optional embodiment of the 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 cylinder sleeve and the lower flange in a disassembled state in Figure 3 is shown;

[0030] Figure 9 A structure schematic diagram of the cylinder sleeve and the lower flange in a disassembled state in Figure 8Structural diagram of eccentricity between cylinder liner and lower flange in

[0031] Figure 10 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 3 Structural diagram of eccentricity between cylinder liner and lower flange in

[0032] Figure 11 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 8 Structural diagram of eccentricity between cylinder liner and lower flange in

[0033] Figure 12 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 11 Structural diagram of eccentricity between cylinder liner and lower flange in

[0034] Figure 13 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 12 Structural diagram of eccentricity between cylinder liner and lower flange in

[0035] Figure 14 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 12 Structural diagram of eccentricity between cylinder liner and lower flange in

[0036] Figure 15 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 14 Structural diagram of eccentricity between cylinder liner and lower flange in

[0037] Figure 16 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 7 Structural diagram of eccentricity between cylinder liner and lower flange in

[0038] Figure 17 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 3 Structural diagram of eccentricity between cylinder liner and lower flange in

[0039] Figure 18 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 1 Structural diagram of eccentricity between cylinder liner and lower flange in

[0040] Figure 19 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 1 Structural diagram of eccentricity between cylinder liner and lower flange in

[0041] Figure 20 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 1 Structural diagram of eccentricity between cylinder liner and lower flange in

[0042] Figure 21 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 1 Structural diagram of eccentricity between cylinder liner and lower flange in

[0043] Figure 22 Structural diagram of eccentricity between cylinder liner and lower flange in Figure 1 Structural diagram of eccentricity between cylinder liner and lower flange in

[0044] Figure 23 a structural schematic diagram showing the cross groove structure in the compressor in the Figure 1

[0045] Figure 24 a structural schematic diagram showing the cross groove structure in the compressor in the Figure 3

[0046] Figure 25 a structural schematic diagram showing the cross groove structure in the compressor in the Figure 3

[0047] Figure 26 a structural schematic diagram showing the cross groove structure in the compressor in the Figure 3

[0048] Figure 27 a structural schematic diagram showing the cross groove structure in the compressor in the

[0049] Figure 28 a structural schematic diagram showing the cross groove structure in the compressor in the

[0050] Figure 29 a structural schematic diagram showing the cross groove structure in the compressor in the

[0051] Figure 30 a structural schematic diagram showing the cross groove structure in the compressor in the

[0052] Figure 31 a structural schematic diagram showing the cross groove structure in the compressor in the

[0053] Figure 32 a structural schematic diagram showing the cross groove structure in the compressor in the

[0054] Figure 33 a structural schematic diagram showing the cross groove structure in the compressor in the

[0055] Figure 34 a structural schematic diagram showing the cross groove structure in the compressor in the Figure 33

[0056] Figure 35 a structural schematic diagram showing the cross groove structure in the compressor in the

[0057] Figure 36 a structural schematic diagram showing the cross groove structure in the compressor in the​​​​​

[0058] Figure 37 A schematic diagram of the mechanism principle of the compressor operation in the Figure 36 is shown, in which a force arm driving the rotation of the slider by the driving shaft is shown;

[0059] Figure 38 A schematic diagram of the mechanism principle of the compressor operation in the Figure 36 is shown, in which the center of the limiting groove structure and the center of the eccentric part coincide.

[0060] Among them, the above-mentioned drawings include the following reference signs:

[0061] 10, crankshaft; 11, eccentric part; 12, shaft body part;

[0062] 20, cylinder sleeve; 21, compression intake port; 22, compression exhaust port; 23, suction cavity; 24, suction communication cavity; 25, exhaust cavity; 26, communication hole;

[0063] 30, cross groove structure; 31, limiting channel; 311, variable volume cavity; 32, center hole;

[0064] 40, slider; 41, through hole; 42, extrusion surface;

[0065] 50, flange; 51, exhaust passage; 52, upper flange; 53, lower flange;

[0066] 60, exhaust valve assembly; 61, exhaust valve plate; 62, valve plate baffle;

[0067] 70, exhaust cover plate;

[0068] 80, distributor component; 81, shell assembly; 82, motor assembly; 83, pump body assembly; 84, upper cover assembly; 85, lower cover assembly;

[0069] 90, fastener. DETAILED DESCRIPTION

[0070] 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, not 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 are within the scope of protection of the present application.

[0071] In the prior art, such as Figure 35As shown, 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.

[0072] In the above operating mechanism principle, the cylinder center O1 and the driving shaft center O2 are the two rotation centers of the operating mechanism, and 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 also makes a reciprocating motion relative to the driving shaft.

[0073] Since the midpoint O0 of the line segment O1O2 is a virtual center, a balance system cannot be set, which leads to the problem of deterioration of the high-frequency vibration characteristics of the compressor. Based on the above operating mechanism principle, as shown, Figure 36 a motion mechanism with O0 as the center of the driving shaft is proposed, that is, the cylinder center O1 and the driving shaft center O0 are the 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.

[0074] Correspondingly, a set of operating mechanisms are proposed, including 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. Specifically, the movement process is as follows: the driving shaft rotates, driving 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.

[0075] However, as shown, Figure 37 the length of the force arm L of the driving shaft driving the slider to rotate is L = 2e x cos θ x cos θ, wherein e is the eccentricity of the eccentric part, and θ is the included angle between the O1O0 connecting line and the sliding direction of the slider in the limiting groove.

[0076] As shown, Figure 38 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.

[0077] Based on this, the application proposes a brand-new mechanism principle with a cross groove structure with two limiting channels 31 and double sliders, and a brand-new compressor is constructed based on the principle, the compressor has the characteristics of high energy efficiency and low noise, and the compressor is taken as an example to introduce the compressor based on the cross groove structure with two limiting channels 31 and double sliders.

[0078] 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 an operation method of the fluid machine, wherein the heat exchange device comprises the fluid machine described below, and the fluid machine is operated by the operation method described below.

[0079] 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 eccentric amounts of the two eccentric parts 11 are 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, 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 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 the crankshaft 10 rotates to drive the slider 40 to reciprocatingly slide in the limiting channel 31 while interacting with the cross groove structure 30, so that the cross groove structure 30 and the slider 40 rotate in the cylinder sleeve 20.

[0080] By setting the cross-groove structure 30 to have a structure form with two limiting channels 31, and corresponding setting two sliders 40, the two eccentric parts 11 of the crankshaft correspondingly extend into the two through holes 41 of the two sliders 40, at the same time, the two sliders 40 are correspondingly slidably arranged in the two limiting channels 31 and form a variable volume cavity 311, since the first included angle A between the two eccentric parts 11 is twice the second included angle B between the extension directions of the two limiting channels 31, so 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 one 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 the 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.

[0081] In addition, the fluid machine provided by the present application can operate stably, that is, the energy efficiency of the compressor is higher and the noise is smaller, thereby ensuring the working reliability of the heat exchange equipment.

[0082] It should be noted that in the present application, the first included angle A and the second included angle B are not zero.

[0083] As Figure 33 and Figure 34As 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.

[0084] 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. The lengths of the first connecting rod L1 and the second connecting rod L2 are equal. (Please refer to...) Figure 33 .

[0085] like Figure 33 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.

[0086] like Figure 34 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 H3 with line O0O1, and the corresponding third connecting rod L3 has a fourth included angle D with line O0O1, wherein the third included angle H3 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 H3 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.

[0087] 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.

[0088] 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, 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, 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, due to the limitation of 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 that the stable operation of the fluid machine is realized, the dead point position of the movement mechanism is avoided, and the movement reliability of the fluid machine is improved, so as to ensure the working reliability of the heat exchange equipment.

[0089] It should be noted that, in the present application, the maximum force arm of the driving torque of the eccentric part 11 is 2e.

[0090] 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.

[0091] It should be noted that, in the present application, in the process of rotating the crankshaft 10, the crankshaft 10 rotates 2 rounds, and 4 times of suction and exhaust processes are completed.

[0092] 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.

[0093] As shown in FIG. 1, the fluid machine comprises a crankshaft 10 and a cross-groove structure 30. Figures 1 to 28As 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.

[0094] Specifically, as shown in the drawings, Figure 6 the eccentricities of the two eccentric parts 11 are both equal to e, as shown in the drawings, Figure 7 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 9 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.

[0095] Optionally, the first assembly gap between the crankshaft 10 and the flange 50 is 0.005mm-0.05mm.

[0096] Preferably, the first assembly gap is 0.01-0.03mm.

[0097] 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.

[0098] 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.

[0099] As shown in the drawings, Figures 2 to 7 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.

[0100] 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.

[0101] Optionally, the first segment and the second segment are detachably connected. In this way, the assembly and disassembly of the crankshaft 10 are facilitated.

[0102] 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.

[0103] 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.

[0104] 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.

[0105] 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.

[0106] Preferably, the first included angle A is 160 degrees, and the second included angle B is 80 degrees.

[0107] Preferably, the first included angle A is 165 degrees, and the second included angle B is 82.5 degrees.

[0108] Preferably, the first included angle A is 170 degrees, and the second included angle B is 85 degrees.

[0109] Preferably, the first included angle A is 175 degrees, and the second included angle B is 87.5 degrees.

[0110] Preferably, the first included angle A is 180 degrees, and the second included angle B is 90 degrees.

[0111] Preferably, the first included angle A is 185 degrees, and the second included angle B is 92.5 degrees.

[0112] Preferably, the first included angle A is 190 degrees, and the second included angle B is 95 degrees.

[0113] Preferably, the first included angle A is 195 degrees, and the second included angle B is 97.5 degrees.

[0114] 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.

[0115] As shown in Figures 2 to 7 , the eccentric portion 11 is cylindrical.

[0116] 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.

[0117] Optionally, the proximal end of the eccentric portion 11 protrudes from the outer circle of the shaft body portion 12 of the crankshaft 10.

[0118] 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.

[0119] 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.

[0120] 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.

[0121] 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.

[0122] 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.

[0123] As shown in Figure 10 , 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.

[0124] 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 10 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 10 The dashed X-line in the diagram represents the circle containing the center of the two arc surfaces.

[0125] Optionally, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20.

[0126] 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.

[0127] Preferably, the difference ranges from -0.02 to 0.02 mm.

[0128] 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.

[0129] Preferably, S 滑块 / S 排 The value is 12 to 18.

[0130] 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.

[0131] Alternatively, the above-mentioned components can be connected by welding, heat fitting, or cold pressing.

[0132] 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 details can be seen from Figure 2 and Figure 3 .

[0133] 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. During the rotation of 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.

[0134] 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.

[0135] As shown in Figures 18 to 23 , during the reciprocating movement of the slider 40 in the limiting channel 31, the slider 40 rotates relative to the cylinder sleeve 20, Figures 18 to 20 During the process that the slider 40 rotates clockwise from 0° to 180°, the variable volume chamber 311 increases, and during the process that the variable volume chamber 311 increases, 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°, 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 21 to 23 During the process that the slider 40 continues to rotate clockwise from 180° to 360°, 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 that 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 61 of the exhaust valve assembly 60 is opened, and the exhaust operation starts, until the compression ends and enters the next cycle.

[0136] As shown in Figures 18 to 23 , the point marked as M is taken as the reference point of the relative movement between the slider 40 and the crankshaft 10, Figure 19represents the process that the slider 40 rotates clockwise from 0 degree to 180 degree, the angle of rotation of the slider 40 is θ1, and the corresponding angle of rotation of the crankshaft 10 is 2θ1. Figure 21 represents the process that the slider 40 continues to rotate clockwise from 180 degree to 360 degree, the angle of rotation of the slider 40 is 180°+θ2, and the corresponding angle of rotation of the crankshaft 10 is 360°+2θ2. Figure 22 represents the process that the slider 40 continues to rotate clockwise from 180 degree to 360 degree, and the variable volume chamber 311 is communicated with the compression exhaust port 22, the angle of rotation of the slider 40 is 180°+θ3, and the corresponding angle of rotation of the crankshaft 10 is 360°+2θ3, that is, the slider 40 rotates one circle, and the corresponding crankshaft 10 rotates two circles, wherein θ1<θ2<θ3.

[0137] Specifically, as shown in Figure 8 , Figures 11 to 23 , the cylinder sleeve 20 has a compression intake port 21 and a compression exhaust port 22, when any slider 40 is in the intake position, the compression intake port 21 is communicated with the corresponding variable volume chamber 311; when any slider 40 is in the exhaust position, the corresponding variable volume chamber 311 is communicated with the compression exhaust port 22.

[0138] As shown in Figures 8 to 14 , Figures 17 to 23 , the inner wall surface of the cylinder sleeve 20 has a suction chamber 23, which is communicated with the compression intake port 21. 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 inhale, so that the compressor can inhale enough, 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.

[0139] 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.

[0140] 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.

[0141] As shown in Figure 8 , Figure 11 , Figure 13 , the suction chamber 23 is two, the two suction chambers 23 are arranged in an axial direction, and the cylinder sleeve 20 further has a suction communication chamber 24, the two suction chambers 23 are communicated with the suction communication chamber 24, and the compression intake port 21 is communicated 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.

[0142] AsFigures 11 to 13 As shown in the drawings, the suction communication cavity 24 extends along the axial direction of the cylinder sleeve 20 by a second preset distance, and at least one end of the suction communication cavity 24 penetrates the axial end surface of the cylinder sleeve 20. In this way, the suction communication cavity 24 is conveniently formed on the end surface of the cylinder sleeve 20, and the machining convenience of the suction communication cavity 24 is ensured.

[0143] As shown in the drawings, Figure 8 , Figures 11 to 23 The outer wall of the cylinder sleeve 20 is provided with an exhaust cavity 25, and the compression exhaust port 22 is connected to the exhaust cavity 25 through the inner wall of the cylinder sleeve 20. The fluid machine further comprises an exhaust valve assembly 60, which is arranged in the exhaust cavity 25 and corresponds to the compression exhaust port 22. In this way, the exhaust cavity 25 is used to accommodate the exhaust valve assembly 60, effectively reducing the occupied space of the exhaust valve assembly 60, reasonably arranging the components, and improving the space utilization of the cylinder sleeve 20.

[0144] As shown in the drawings, Figures 13 to 17 The compression exhaust port 22 is two, and the two compression exhaust ports 22 are arranged in the axial direction of the cylinder sleeve 20. The exhaust valve assembly 60 is two groups, and the two groups of exhaust valve assemblies 60 are arranged corresponding to the two compression exhaust ports 22. In this way, since the two compression exhaust ports 22 are respectively provided with two groups of exhaust valve assemblies 60, the gas in the variable volume chamber 311 is effectively prevented from leaking in large quantities, and the compression efficiency of the variable volume chamber 311 is ensured.

[0145] As shown in the drawings, Figure 14 The exhaust valve assembly 60 is connected to the cylinder sleeve 20 through a fastener 90, and the exhaust valve assembly 60 comprises an exhaust valve plate 61 and a valve plate baffle 62. The exhaust valve plate 61 is arranged in the exhaust cavity 25 and shields the corresponding compression exhaust port 22, and the valve plate baffle 62 is arranged on the exhaust valve plate 61. In this way, the arrangement of the valve plate baffle 62 effectively prevents the exhaust valve plate 61 from being opened too much, thereby ensuring the exhaust performance of the cylinder sleeve 20.

[0146] Optionally, the fastener 90 is a screw.

[0147] As shown in the drawings, Figure 8 , Figure 11 , Figure 16 and Figure 17 The 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 fluid machine further comprises a flange 50, the flange 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.

[0148] As shown in the drawings, Figure 17As shown, the exhaust cavity 25 penetrates through the outer wall surface of the cylinder sleeve 20, and the fluid machine further comprises an exhaust cover plate 70 connected with the cylinder sleeve 20 and sealing the exhaust cavity 25. In this way, the exhaust cover plate 70 functions to separate the variable volume cavity 311 from the external space of the pump body assembly 83.

[0149] As shown in Figure 16 and Figure 17 When the variable volume cavity 311 is communicated with the compression exhaust port 22 and the pressure of the variable volume cavity 311 reaches the exhaust pressure, the exhaust valve 61 is opened, the compressed gas enters the exhaust cavity 25 through the compression exhaust port 22, and then passes through the communication hole 26 on the cylinder sleeve 20, and is discharged through the exhaust passage 51 and enters the external space of the pump body assembly 83 (i.e. the cavity of the compressor), thereby completing the exhaust process.

[0150] Optionally, the exhaust cover plate 70 is fixed on the cylinder sleeve 20 by fasteners 90.

[0151] Optionally, the fasteners 90 are screws.

[0152] Optionally, the outer contour of the exhaust cover plate 70 is matched with the outer contour of the exhaust cavity 25.

[0153] The operation of the compressor will be described in detail as follows:

[0154] As shown in Figure 1 The motor assembly 82 drives the rotation of the crankshaft 10, and the two eccentric parts 11 of the crankshaft 10 drive the corresponding two sliders 40 to move, respectively. 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 passage 31 and drives the cross groove structure 30 to rotate in the cylinder sleeve 20. The slider 40 revolves while reciprocating along the limiting passage 31 to form a cross slider mechanism movement mode.

[0155] Other use occasions: The compressor can be used as an expander by exchanging the positions of the suction and exhaust ports. That is, the exhaust port of the compressor is used as the suction port of the expander, high-pressure gas is introduced, and other driving mechanisms rotate to discharge the gas after expansion through the suction port of the compressor (the exhaust port of the expander).

[0156] When the fluid machine is an expander, the cylinder sleeve 20 has an expansion exhaust port and an expansion intake port, the expansion exhaust port is communicated with the corresponding variable volume chamber 311 when any one of the sliders 40 is in the intake position; the corresponding variable volume chamber 311 is communicated with the expansion intake port when any one of the sliders 40 is in the exhaust position. In this way, when 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 is linearly slid 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 consumption equipment, the crankshaft 10 can output power.

[0157] Optionally, the inner wall surface of the cylinder sleeve 20 has an expansion exhaust chamber, and the expansion exhaust chamber is communicated with the expansion exhaust port.

[0158] Further, the expansion exhaust chamber 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 chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion intake port is located, and the extension direction of the expansion exhaust chamber is the same as the rotation direction of the cross groove structure 30.

[0159] Further, the expansion exhaust chamber is two, the two expansion exhaust chambers are arranged in the axial direction of the cylinder sleeve 20, and the cylinder sleeve 20 further has an expansion exhaust communication chamber, the two expansion exhaust chambers are communicated with the expansion exhaust communication chamber, and the expansion exhaust port is communicated with the expansion exhaust chamber through the expansion exhaust communication chamber.

[0160] Further, the expansion exhaust communication chamber 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 chamber penetrates the axial end surface of the cylinder sleeve 20.

[0161] In order to solve the problem of how to prevent the gap leakage and wear of the pump body assembly, the fluid machine further comprises the following features on the basis of the above fluid machine, and the specific embodiments are as follows:

[0162] As shown in Figure 2 , Figure 3 , Figure 12 , Figure 24 , Figures 27 to 29 , the fluid machine further comprises two flanges 50, the two flanges 50 are arranged at the two axial ends of the cylinder sleeve 20; the cross groove structure 30 is coaxially arranged with the cylinder sleeve 20, and the outer circumferential surface of the cross groove structure 30 and the inner wall surface of the cylinder sleeve 20 have a first radial gap, the range of the first radial gap is 0.005mm-0.1mm, the height H3 of the cylinder sleeve 20 and the height H2 of the cross groove structure 30 have a difference, and the range of the difference is 0.008mm-0.05mm.

[0163] By optimizing the range of the first radial gap between the outer circumferential surface of the cross groove structure 30 and the inner wall surface of the cylinder sleeve 20, the power consumption of the fluid machine can be ensured to reach the optimal value; in addition, by optimizing the range of the difference between the height H3 of the cylinder sleeve 20 and the height H2 of the cross groove structure 30, the gap fit between the end surface of the axial both ends of the cross groove structure 30 and the end surface of the axial both ends of the cylinder sleeve 20 is ensured, and the gap fit between the end surface of the axial both ends of the cross groove structure 30 and the surface of the two flanges 50 on the side facing the cylinder sleeve 20 is ensured, avoiding the phenomenon of jamming and wear of the cross groove structure 30 during rotation, which is beneficial to reduce the power consumption of the fluid machine, while ensuring the sealing performance and refrigeration capacity of the fluid machine.

[0164] Preferably, the range of the first radial gap is 0.01-0.06mm.

[0165] Preferably, the range of the difference is 0.01mm-0.03mm.

[0166] As shown in Figures 2 to 5 , the projection of the sliding block 40 in the sliding direction thereof is square; the cross section of the limiting channel 31 in the sliding direction of the sliding block 40 is square.

[0167] As shown in Figure 25 , Figure 26 , Figure 30 , the difference between the width B1 of the limiting channel 31 and the width B2 of the sliding block 40 is B1-B2, wherein the range of B1-B2 is 0.005mm-0.05mm. In this way, the sliding reliability of the sliding block 40 in the limiting channel 31 is ensured on the premise of ensuring the sealing reliability of the pump body assembly 83.

[0168] Preferably, the range of B1-B2 is 0.01mm-0.02mm.

[0169] As shown in Figures 25 to 28 , the difference between the height H of the sliding block 40 and the depth H1 of the limiting channel 31 is H-H1, wherein the range of H-H1 is 0mm-0.05mm. In this way, by reasonably optimizing the range of H-H1, sufficient gap between the two is ensured, which not only ensures the smooth sliding of the sliding block 40 in the limiting channel 31 of the cross groove structure 30, but also ensures that the gap between the two does not affect the sealing performance of the pump body assembly 83 and the refrigeration capacity of the compressor.

[0170] Preferably, the range of H-H1 is 0.01mm-0.02mm.

[0171] As shown in Figure 25As shown, the ratio of the depth H1 of the limiting channel 31 to the width B1 of the limiting channel 31 is H1 / B1, wherein the range of H1 / B1 is 0.3-1.2. In this way, by reasonably optimizing the ratio H1 / B1 of the depth H1 of the limiting channel 31 to the width B1 of the limiting channel 31, the friction area between the cross-groove structure 30 and the sliding block 40 can be ensured to be within a reasonable range, thereby ensuring that the power consumption can reach an optimal value.

[0172] It should be noted that in the present application, considering that the end face of the cross-groove structure 30 is an acute angle and is easy to scratch the end face of the flange 50 after being inclined, at the same time, the outer diameter of the cross-groove structure 30 is relatively large and the linear speed is relatively large, the direct contact between the cross-groove structure 30 and the end face of the flange 50 leads to relatively large friction power consumption therebetween, based on the above two points, in actual design, the height of the sliding block 40 is not less than the height of the end face of the cross-groove structure 30, so that the sliding block 40 is in contact with the end face of the flange 50 first, thereby realizing the improvement of the reliability of the compressor and the reduction of the friction power consumption.

[0173] Specifically, as shown in Figure 27 and Figure 28 , the height H of the sliding block 40 in the axial direction of the cross-groove structure 30 is greater than or equal to the height H1 of the limiting channel 31 in the axial direction of the cross-groove structure 30. In this way, among them, Figure 27 , the height H of the sliding block 40 in the axial direction of the cross-groove structure 30 is greater than the height H1 of the limiting channel 31 in the axial direction of the cross-groove structure 30, Figure 28 , the height H of the sliding block 40 in the axial direction of the cross-groove structure 30 is equal to the height H1 of the limiting channel 31 in the axial direction of the cross-groove structure 30.

[0174] It should be noted that in the present application, the ratio of the eccentric amount e of the eccentric part 11 to the outer radius D / 2 of the cross-groove structure 30 is e / D / 2, wherein the range of e / D / 2 is 0.02-0.06. In this way, the above e / D / 2 is the eccentricity ratio of the cross-groove structure 30, and ensuring that the eccentricity ratio is within the above range makes the torque of the crankshaft 10 optimal, thereby controlling the power consumption of the compressor to be within a suitable range.

[0175] It should be noted that in the present application, considering that the main friction surface of the cross-groove structure 30 during rotation is its outer circumferential surface, and the outer circumferential surface area is determined by the height H2 of the cross-groove structure 30 and the outer diameter D, and the larger the outer diameter D is, the longer the force arm of the torque received by the cross-groove structure 30 is, in order to make the torque received by the crankshaft 10 and the friction area of the cross-groove structure 30 balanced, thereby making the power consumption of the compressor optimal, as shown in Figure 24 , Figure 25 and Figure 31As shown, the ratio of the height H2 of the cross groove structure 30 to the outer diameter D of the cross groove structure 30 is H2 / D, wherein the range of H2 / D is 0.4-2. In this way, the above-mentioned H2 / D is the height-diameter ratio of the cross groove structure 30, and ensuring that the height-diameter ratio is within the above-mentioned range can make the power consumption of the compressor optimal.

[0176] As shown in FIG. 1, the cross groove structure 30 is arranged in the cylinder sleeve 20, and the cross groove structure 30 is arranged in the cylinder sleeve 20 in a manner of being in contact with the inner wall of the cylinder sleeve 20. Figure 25 and Figure 32 As shown, the sealing distance F between the two limiting channels 31 of the cross groove structure 30 ranges from 1 mm to 15 mm. In this way, by optimizing the sealing distance F between the two limiting channels 31, it is avoided that the sealing distance F is too small to ensure the sealing of the inner cavities of the two limiting channels 31, resulting in the phenomenon of air leakage between the upper and lower sliders 40, thereby causing the inward leakage of back pressure and repeated compression, and further resulting in the loss of refrigeration capacity and the output of additional power consumption; it is also avoided that the sealing distance F is too large to increase the outer circular surface area of the cross groove structure 30, i.e., to increase the friction pair area between the cross groove structure 30 and the inner circle of the cylinder sleeve 20, thereby increasing the friction loss.

[0177] It should be noted that the shortest distance between the two limiting channels 31 in Figure 25 is defined as the sealing distance F.

[0178] It should be noted that the terms used herein are only intended to describe 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 be understood that, when the terms "comprise" and / or "include" are used in the specification, there is a presence of the features, steps, operations, devices, components and / or combinations thereof.

[0179] The relative arrangement of the components and steps, numerical expressions, and numerical 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 proportion to the actual proportions. The techniques, methods and devices known to those skilled in the relevant art can not be discussed in detail, but should be considered as part of the authorized specification, if appropriate. 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, and therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0180] 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, or the like, directional terms are used in the description herein (e.g., "forward", "rearward", "up", "down", "left", "right", "vertical", "horizontal", "upper", "lower", "above", "below", "upward", "downward", "top", "bottom" and the like), it is understood that these terms are used to facilitate the description of the application, and do not limit the scope of the application. For example, if the application is turned over, or rotated 90 degrees, or inverted, the directional terms are reversed. Accordingly, the directional terms are interchangeable under appropriate circumstances such that the application described herein describes the application in one orientation, and is equally applicable to other orientations, unless otherwise specifically noted.

[0181] It is also important to note that the term "or" as used herein is intended to mean any of the possible options. For example, if X or Y or both are present, that covers the options of X being present and Y being absent, Y being present and X being absent, and both X and Y being present.

[0182] It should be noted that the terms "first", "second", and the like, herein do not necessarily have an either / then meaning, but are used to distinguish one element from another. It should be understood that the use of these terms "first", "second", and the like, are used herein to distinguish between two or more similar elements, and are not used to designate a particular order or sequence. Unless otherwise specified, the use of these terms "first", "second", and the like, is not intended to limit the scope of the application to only a single sequence.

[0183] The specific embodiments described herein are illustrative and not intended to be limiting. Other embodiments will readily occur to those skilled in the art. Modifications can be made to adapt a particular situation to the teachings of the present disclosure without departing from the central inventive concept described herein. Therefore, it is meant to cover any variations, uses or adaptations of the application following, in general, the principles of the application, and including such departures from the present disclosure that come within known or customary practice in the art to which the application pertains.

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 of the crankshaft (10); a cylinder sleeve (20) eccentrically arranged with the crankshaft (10) and fixed in eccentric distance; a cross-groove structure (30) rotatably arranged in the cylinder sleeve (20) and coaxially arranged with the cylinder sleeve (20), wherein a first radial gap is formed between the outer circumferential surface of the cross-groove structure (30) and the inner wall surface of the cylinder sleeve (20), the range of the first radial gap is 0.005mm-0.1mm, the height H3 of the cylinder sleeve (20) and the height H2 of the cross-groove structure (30) have a difference, the range of the difference is 0.008mm-0.05mm, 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), and the crankshaft (10) rotates to drive the sliders (40) to reciprocatingly slide in the limiting channels (31) and interact 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) arranged at the two axial ends of the cylinder sleeve (20) respectively.

2. The fluid machine of claim 1, wherein, The range of the first radial gap is 0.01-0.06mm.

3. The fluid machine of claim 1, wherein, The range of the difference is 0.01mm-0.03mm.

4. The fluid machine according to claim 1, wherein the projection of the slider (40) in the sliding direction thereof is square-shaped; the cross section of the limiting channel (31) in the sliding direction of the slider (40) is square-shaped.

5. The fluid machine of claim 4, wherein, The difference between the width B1 of the limiting channel (31) and the width B2 of the slider (40) is B1-B2, wherein the range of B1-B2 is 0.005mm-0.05mm.

6. The fluid machine of claim 5, wherein, The range of B1-B2 is 0.01mm-0.02mm.

7. The fluid machine of claim 4, wherein, The difference between the height H of the slider (40) and the depth H1 of the limiting channel (31) is H-H1, wherein the range of H-H1 is 0mm-0.05mm.

8. The fluid machine of claim 7, wherein, The range of H-H1 is 0.01mm-0.02mm.

9. The fluid machine of claim 1, wherein, The ratio of the depth H1 of the limiting channel (31) to the width B1 of the limiting channel (31) is H1 / B1, wherein the range of H1 / B1 is 0.3-1.

2.

10. The fluid machine of claim 1, wherein, The ratio of the eccentricity e of the eccentric part (11) to the outer circle radius D / 2 of the cross groove structure (30) is e / D / 2, wherein the range of e / D / 2 is 0.02-0.

06.

11. The fluid machine of claim 1, wherein, The ratio of the height H2 of the cross groove structure (30) to the outer circle diameter D of the cross groove structure (30) is H2 / D, wherein the range of H2 / D is 0.4-2.

12. The fluid machine of claim 1, wherein, The sealing distance F between the two limiting channels (31) of the cross groove structure (30) ranges from 1mm to 15mm.

13. The fluid machine of any one of claims 1 to 12, wherein, The phase difference between the two eccentric parts (11) has a first included angle A, the eccentricities of the two eccentric parts (11) are equal, and the phase difference between the extension directions 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 according to any one of claims 1-13.

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