Fluid machine and heat exchange device

Abstract

The application provides a fluid machine and a heat exchange device, the fluid machine comprising a crankshaft, a cylinder sleeve, a cross groove structure, a sliding block and two flanges, the crankshaft having two eccentric parts; the crankshaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed; two limiting channels of the cross groove structure are sequentially arranged along the axial direction of the crankshaft, and the extension 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; at least one of the two flanges is provided with a first axial exhaust hole, and at least one of the two flanges is provided with a second axial exhaust hole; wherein, at least one of the two ends of the cylinder sleeve in the axial direction has a bevel at the edge of the inner circle, the bevel is communicated with the first axial exhaust hole, and the side wall surface of the cylinder sleeve has at least one exhaust port, the exhaust port is communicated with the second axial exhaust hole. The application solves the problems of low energy efficiency, large noise and how to reduce exhaust loss of the compressor in the prior art.

Description

TECHNICAL FIELD

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

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

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

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

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

[0006] In order to achieve the above-mentioned purpose, according to one aspect of the present application, a fluid machine is provided, comprising a crankshaft, a cylinder sleeve, a cross groove structure, a sliding block and two flanges, the crankshaft is provided with two eccentric parts along 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 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 ends of the cylinder sleeve respectively, at least one of the two flanges is provided with a first axial exhaust hole, and at least one of the two flanges is provided with a second axial exhaust hole; wherein, the edge of the inner circle of at least one end of the axial ends of the cylinder sleeve has an oblique notch, the oblique notch is communicated with the first axial exhaust hole, and the side wall surface of the cylinder sleeve has at least one exhaust port, the exhaust port is communicated with the second axial exhaust hole.

[0007] Further, the first axial exhaust hole and the second axial exhaust hole on the same flange are on the same radius of the flange, and the second axial exhaust hole is located on the outer peripheral side of the first axial exhaust hole.

[0008] Further, the first axial exhaust hole is arranged on the flange at one end of the bevel cutout.

[0009] Further, the geometric center line of the first axial exhaust hole passes through the geometric center of the bevel cutout.

[0010] Further, the projection of the sliding block in the sliding direction thereof is a part of a semicircle; and / or, the projection of the sliding block in the axial direction of the through hole has two opposite parallel straight line segments and an arc segment connecting the end portions of the two straight line segments; and the arrangement position of the exhaust port in the circumferential direction of the cylinder sleeve is within an angle range of (arccos(2R / B)~2×arccos(2R / B)), wherein R is the inner circle radius of the cylinder sleeve, and B is the distance between the two opposite parallel straight line segments of the projection of the sliding block in the axial direction of the through hole.

[0011] Further, the exhaust cavity is arranged on the outer wall of the cylinder sleeve, the exhaust port is communicated to the exhaust cavity through the inner wall of the cylinder sleeve, the fluid machine further comprises an exhaust valve assembly arranged in the exhaust cavity and corresponding to the exhaust port; and the cylinder sleeve is further provided with a communication hole on the axial end surface thereof, the communication hole being communicated with the exhaust cavity and the second axial exhaust hole.

[0012] Further, the distance between the plane where the exhaust port is communicated with the exhaust cavity and the axis of the cylinder sleeve is K, and the inner circle radius of the cylinder sleeve is R, wherein 1mm≦K-R≦5mm.

[0013] Further, the cavity sectional area of the exhaust cavity in the axial direction of the cylinder sleeve is S3, the height of the exhaust cavity in the axial direction of the cylinder sleeve is N, and the displacement of the fluid machine is V, wherein 0.2≦(N×S3) / V≦5.

[0014] Further, the exhaust cavity is arranged on the outer wall of the cylinder sleeve, the boss structure is arranged on the cavity wall surface of the exhaust cavity, and the exhaust port is communicated to the boss structure through the inner wall of the cylinder sleeve and communicated with the exhaust cavity.

[0015] Further, the thickness of the boss structure in the extension direction of the exhaust port is M, wherein 0.05mm≦M≦3mm.

[0016] Further, the sectional area of the hole section of the exhaust port is S1, and the volume of the single variable volume chamber is V1, wherein 750≦V1 / S1≦3300.

[0017] Further, the inclination direction of the bevel cutout is along the end surface of the axial end of the cylinder sleeve towards the axis of the cylinder sleeve, and the included angle between the bevel cutout and the end surface of the cylinder sleeve is α, wherein 15°≦α≦60°.

[0018] Further, the equivalent diameter of the circle where the bevel cut is located is D, and the volume of the single variable volume chamber is V1, wherein 400≦V1 / D≦1000.

[0019] Further, the longitudinal section of the bevel cut across the diameter of the cylinder liner coincides with the longitudinal section of the exhaust port across the diameter of the cylinder liner.

[0020] Further, the cross-sectional area of the hole section of the first axial exhaust port is S4, and the volume of the single variable volume chamber is V1, wherein 750≦V1 / S4≦3300; and / or, the cross-sectional area of the hole section of the second axial exhaust port is S2, and the volume of the single variable volume chamber is V1, wherein 50≦V1 / S2≦250.

[0021] Further, the exhaust cavity penetrates to the outer wall surface of the cylinder liner, and the fluid machine further comprises an exhaust cover plate connected with the cylinder liner and sealing the exhaust cavity.

[0022] 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 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.

[0023] According to another aspect of the present application, a heat exchange device is provided, comprising the fluid machine as described above.

[0024] By the technical scheme of the present application, at least one of the two flanges is provided with a first axial exhaust hole, at least one of the two flanges is provided with a second axial exhaust hole; at least one of the inner circles of the axial two ends of the cylinder liner has a bevel cut at the edge thereof, the bevel cut is communicated with the first axial exhaust hole, the side wall surface of the cylinder liner has at least one exhaust port, and the exhaust port is communicated with the second axial exhaust hole. In this way, the exhaust reliability of the fluid machine is ensured, the exhaust loss of the fluid machine is reduced, and the efficiency of the fluid machine is improved. BRIEF DESCRIPTION OF DRAWINGS

[0025] The drawings accompanying the specification of the present application form a part thereof, serve to provide further understanding of the present application, and together with the specification explain the application. The use of these drawings in explaining the application does not imply that the present application should be limited to the embodiments illustrated therein. In the drawings:

[0026] Figure 1 An internal structure schematic diagram of a compressor according to Embodiment One of the present application is shown;

[0027] Figure 2 A structure schematic diagram of a pump body assembly of a compressor in Figure 1 is shown;

[0028] Figure 3 A structure schematic diagram of a pump body assembly of a compressor in Figure 2exploded structural diagram of the pump body assembly in the pump;

[0029] Figure 4 illustrates Figure 3 assembly structural diagram of the crankshaft, cross groove structure, slider in the pump;

[0030] Figure 5 illustrates Figure 4 cross-sectional structural diagram of the crankshaft, cross groove structure, slider in the pump;

[0031] Figure 6 illustrates Figure 4 structural diagram of the shaft body part of the crankshaft and the eccentric amount of the two eccentric parts in the pump;

[0032] Figure 7 illustrates Figure 3 cross-sectional structural diagram of the assembly eccentric amount of the crankshaft and the cylinder liner in the pump;

[0033] Figure 8 illustrates Figure 3 structural diagram of the eccentric amount between the cylinder liner and the lower flange in the pump;

[0034] Figure 9 illustrates Figure 3 structural diagram of the slider in the pump in the axial direction of the through hole;

[0035] Figure 10 illustrates Figure 3 structural diagram of the state of the compressor in the pump at the beginning of suction;

[0036] Figure 11 illustrates Figure 3 structural diagram of the state of the compressor in the pump during suction;

[0037] Figure 12 illustrates Figure 3 structural diagram of the state of the compressor in the pump at the end of suction;

[0038] Figure 13 illustrates Figure 3 structural diagram of the state of the compressor in the pump when compressing gas;

[0039] Figure 14 illustrates Figure 3 structural diagram of the state of the compressor in the pump during exhaust;

[0040] Figure 15 illustrates Figure 3 structural diagram of the state of the compressor in the pump at the end of exhaust;

[0041] Figure 16 illustrates Figure 3 structural diagram of the cylinder liner in the pump;

[0042] Figure 17 It shows Figure 3 A cross-sectional view of the cylinder liner is shown in the figure, which illustrates the range of the exhaust port's circumferential angle in the cylinder liner.

[0043] Figure 18 It shows Figure 3 A cross-sectional view of the cylinder liner is shown in the figure, which illustrates the relationship between K and R.

[0044] Figure 19 It shows Figure 3 A cross-sectional view of the cylinder liner is shown in the figure, which illustrates the range of angles at which the oblique cut is positioned in the circumferential direction of the cylinder liner.

[0045] Figure 20 It shows Figure 3 A cross-sectional view of the cylinder liner from another perspective, showing the angle between the bevel and the end face of the cylinder liner;

[0046] Figure 21 It shows Figure 3 A top-view structural diagram of the upper flange;

[0047] Figure 22 It shows Figure 2 Another cross-sectional view of the pump body assembly shows an assembly misalignment of e between the crankshaft and the cylinder liner.

[0048] Figure 23 It shows Figure 3 A schematic diagram of the exhaust chamber side of the cylinder liner;

[0049] Figure 24 It shows Figure 2 A cross-sectional view of the cylinder liner is shown in the figure. The cross groove structure, slider, and crankshaft are omitted in the figure.

[0050] Figure 25 A schematic diagram of the exhaust chamber side of a cylinder liner according to an optional embodiment of the present invention is shown, in which a boss structure is provided at the exhaust port;

[0051] Figure 26 It shows Figure 25 A partial cross-sectional view of the cylinder liner in the diagram;

[0052] Figure 27 It shows Figure 3 A schematic diagram of the cross-section of the slider in its sliding direction;

[0053] Figure 28 A schematic diagram of the pump body assembly according to Embodiment 2 of the present invention is shown;

[0054] Figure 29 Fig. 3 shows a structural schematic diagram of a pump body assembly according to an embodiment of the present application;

[0055] Figure 30 Fig. 4 shows a structural schematic diagram of a pump body assembly according to an embodiment of the present application;

[0056] Figure 31 Fig. 5 shows a structural schematic diagram of a pump body assembly according to an embodiment of the present application;

[0057] Figure 32 Fig. 6 shows a structural schematic diagram of a pump body assembly according to an embodiment of the present application;

[0058] Figure 33 Fig. 7 shows a structural schematic diagram of a pump body assembly according to an embodiment of the present application;

[0059] Figure 34 Fig. 8 shows a structural schematic diagram of a pump body assembly according to an embodiment of the present application;

[0060] Figure 35 Fig. 9 shows a schematic diagram of the mechanism of a compressor operation according to an alternative embodiment of the present application;

[0061] Figure 36 Fig. 10 shows a schematic diagram of the mechanism of a compressor operation in the prior art; Figure 35

[0062] Figure 37 Fig. 11 shows a schematic diagram of the mechanism of a compressor operation in the prior art;

[0063] Figure 38 Fig. 12 shows a schematic diagram of the mechanism of an improved compressor operation in the prior art;

[0064] Figure 39 Fig. 13 shows a schematic diagram of the mechanism of a compressor operation in Figure 38

[0065] Figure 40 Fig. 14 shows a schematic diagram of the mechanism of a compressor operation in Figure 38

[0066] Fig. 15 shows a schematic diagram of the variation of the exhaust loss, COP, and clearance volume of a compressor with V1 / S1. Figure 41

[0067] Fig. 15 shows a schematic diagram of the variation of the exhaust loss, COP, and clearance volume of a compressor with V1 / S1.

[0068] 10, crankshaft; 11, eccentric part; 12, shaft body portion; 10, crankshaft; 11, eccentric part; 12, shaft body portion;​​

[0069] 20, cylinder liner; 21, radial suction hole; 22, exhaust port; 23, suction chamber; 24, suction communication chamber; 25, exhaust chamber; 26, communication hole; 27, bevel cut; 29, boss structure;

[0070] 30, cross groove structure; 31, limiting channel; 311, variable volume chamber; 32, center hole;

[0071] 40, slider; 41, through hole; 42, extrusion surface;

[0072] 50, flange; 511, first axial exhaust hole; 512, second axial exhaust hole; 52, upper flange; 53, lower flange;

[0073] 70, exhaust cover plate;

[0074] 80, distributor component; 81, housing assembly; 82, motor assembly; 83, pump body assembly; 84, upper cover assembly; 85, lower cover assembly. DETAILED DESCRIPTION

[0075] The technical solutions in the embodiments of the present application will be clearly and completely described with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. The description of the at least one exemplary embodiment is actually only illustrative, but not as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative labor fall within the scope of protection of the present application.

[0076] In the prior art, as shown in Figure 37 , 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.

[0077] 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.

[0078] 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. Based on the above operating mechanism principle, as shown in Figure 38As 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.

[0079] Correspondingly, a set of operation mechanism is proposed, which comprises a cylinder, a limiting groove structure, a slider and a driving shaft, wherein the limiting groove structure is rotatably arranged in the cylinder, and the cylinder and the limiting groove structure are coaxially arranged, that is, the cylinder center O1 is also the center of the limiting groove structure, the slider reciprocates relative to the limiting groove structure, the slider is coaxially assembled with the eccentric part of the driving shaft, and the slider makes a circular motion around the shaft body part of the driving shaft, and specifically, the motion process is as follows: the driving shaft rotates to drive the slider to revolve around the center of the shaft body part of the driving shaft, the slider simultaneously rotates relative to the eccentric part, and the slider reciprocates in the limiting groove of the limiting groove structure and drives the limiting groove structure to rotate.

[0080] However, as shown in the prior art, Figure 39 The length of the force arm L of the driving shaft driving the slider to rotate is L=2e*cos theta*cos theta, wherein e is the eccentricity of the eccentric part, and theta is the included angle between the O1O0 line and the sliding direction of the slider in the limiting groove.

[0081] As shown in the prior art, Figure 40 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.

[0082] 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, and the compressor 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.

[0083] 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 equipment and a running method of the fluid machine, wherein the heat exchange equipment comprises the fluid machine described below, and the fluid machine runs by using the running method described below.

[0084] The fluid machine in the application comprises a crankshaft 10, a cylinder sleeve 20, a cross groove structure 30 and a slider 40, wherein the crankshaft 10 is provided with two eccentric parts 11 along the axial direction of the crankshaft 10, the two eccentric parts 11 have a phase difference of a first included angle A, and the eccentricity of the two eccentric parts 11 is equal; the crankshaft 10 is eccentrically arranged with the cylinder sleeve 20 and the eccentric distance is fixed; the cross groove structure 30 is rotatably arranged in the cylinder sleeve 20, the cross groove structure 30 has two limiting channels 31, the two limiting channels 31 are sequentially arranged along the axial direction of the crankshaft 10, the extension direction of the limiting channel 31 is perpendicular to the axial direction of the crankshaft 10, and the extension directions of the two limiting channels 31 have a phase difference of a second included angle B, wherein the first included angle A is twice the second included angle B; the slider 40 has a through hole 41, and there are two sliders 40, the two eccentric parts 11 correspondingly extend into the two through holes 41 of the two sliders 40, the two sliders 40 are correspondingly arranged to slide in the two limiting channels 31 and form a variable volume cavity 311, the variable volume cavity 311 is located in the sliding direction of the slider 40, and when the crankshaft 10 rotates to drive the slider 40 to reciprocally slide in the limiting channel 31, the cross groove structure 30 and the slider 40 rotate in the cylinder sleeve 20.

[0085] By arranging the cross groove structure 30 in the form of two limiting channels 31 and correspondingly arranging two sliders 40, the two eccentric parts 11 of the crankshaft correspondingly extend into the two through holes 41 of the two sliders 40, and at the same time, the two sliders 40 are correspondingly arranged to slide in the two limiting channels 31 and form a variable volume cavity 311, since the first included angle A between the two eccentric parts 11 is twice the second included angle B between the extension directions of the two limiting channels 31, when one of the two sliders 40 is at the dead center position, the driving torque of the eccentric part 11 corresponding to the slider 40 at the dead center position is 0, and the slider 40 at the dead center position cannot continue to rotate, while the driving torque of the other eccentric part 11 of the two eccentric parts 11 driving the corresponding slider 40 is the maximum value, which ensures that the eccentric part 11 with the maximum driving torque can normally drive the corresponding slider 40 to rotate, thereby driving the cross groove structure 30 to rotate through the slider 40, and further driving the slider 40 at the dead center position to continue to rotate through the cross groove structure 30, realizing stable operation of the fluid machine, avoiding the dead center position of the motion mechanism, and improving the motion reliability of the fluid machine, thereby ensuring the working reliability of the heat exchange equipment.

[0086] In addition, the fluid machine provided by the 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.

[0087] It should be noted that in the application, the first included angle A and the second included angle B are not zero.

[0088] As Figure 35And Figure 36 As shown in the above fluid machine operation, the crankshaft 10 rotates around the axis O0 of the crankshaft 10; the cross groove structure 30 revolves around the axis O0 of the crankshaft 10, the axis O0 of the crankshaft 10 and the axis O1 of the cross groove structure 30 are eccentrically arranged and the eccentric distance is fixed; the first slider 40 makes a circular motion with the axis O0 of the crankshaft 10 as the 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 eccentric amount of the corresponding first eccentric part 11 of the crankshaft 10, and the eccentric amount 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 first slider 40 to make a circular motion, and the first slider 40 interacts with the cross groove structure 30 and reciprocally slides in 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 eccentric amount of the corresponding second eccentric part 11 of the crankshaft 10, and the eccentric amount 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 reciprocally slides in the limiting channel 31 of the cross groove structure 30.

[0089] As shown in the above fluid machine operation, the crankshaft 10 rotates around the axis O0 of the crankshaft 10; the cross groove structure 30 revolves around the axis O0 of the crankshaft 10, the axis O0 of the crankshaft 10 and the axis O1 of the cross groove structure 30 are eccentrically arranged and the eccentric distance is fixed; the first slider 40 makes a circular motion with the axis O0 of the crankshaft 10 as the 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 eccentric amount of the corresponding first eccentric part 11 of the crankshaft 10, and the eccentric amount 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 first slider 40 to make a circular motion, and the first slider 40 interacts with the cross groove structure 30 and reciprocally slides in 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 eccentric amount of the corresponding second eccentric part 11 of the crankshaft 10, and the eccentric amount 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 reciprocally slides in the limiting channel 31 of the cross groove structure 30. Figure 35 ).

[0090] As Figure 35 shown, the first angle A between the first link L1 and the second link L2 is twice the second angle B between the third link L3 and the fourth link L4.

[0091] As Figure 36 shown, the line connecting the axis O0 of the crankshaft 10 and the axis O1 of the cross groove structure 30 is the line O0 O1, the third angle C between the first link L1 and the line O0 O1 is twice the fourth angle D between the corresponding third link L3 and the line O0 O1; the fifth angle E between the second link L2 and the line O0 O1 is twice the sixth angle F between the corresponding fourth link L4 and the line O0 O1; the sum of the third angle C and the fifth angle E is the first angle A, and the sum of the fourth angle D and the sixth angle F is the second angle B.

[0092] 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.

[0093] 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, and improve the movement reliability of the fluid machine, so as to ensure the working reliability of the heat exchange equipment.

[0094] It should be noted that, in the present application, the maximum force arm of the driving torque of the eccentric part 11 is 2e.

[0095] 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.

[0096] It should be noted that, in the present application, in the process of the rotation of the crankshaft 10, the crankshaft 10 rotates 2 rounds, and completes 4 times of suction and exhaust processes.

[0097] 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.

[0098] Embodiment one

[0099] As Figures 1 to 27 shown, the fluid machine further comprises a flange 50, the flange 50 is arranged at the axial end of the cylinder sleeve 20, the crankshaft 10 is arranged concentrically with the flange 50, the cross groove structure 30 is arranged coaxially with the cylinder sleeve 20, and the assembly eccentricity of the crankshaft 10 and the cross groove structure 30 is determined by the relative position relationship of the flange 50 and the cylinder sleeve 20, wherein the flange 50 is fixed on the cylinder sleeve 20 by fasteners, the relative position of the axis of the flange 50 and the axis of the inner ring of the cylinder sleeve 20 is controlled by centering the flange 50, and the relative position of the axis of the flange 50 and the axis of the inner ring of the cylinder sleeve 20 determines the relative position of the axis of the crankshaft 10 and the axis of the cross groove structure 30. The essence of centering the flange 50 is to make the eccentricity of the eccentric part 11 equal to the assembly eccentricity of the crankshaft 10 and the cylinder sleeve 20.

[0100] Specifically, as Figure 6 shown, the eccentricity of the two eccentric parts 11 is equal to e, as Figure 7 shown, the assembly eccentricity between the crankshaft 10 and the cylinder sleeve 20 is e (since the cross groove structure 30 is arranged coaxially with the cylinder sleeve 20, the assembly eccentricity between the crankshaft 10 and the cross groove structure 30 is the assembly eccentricity between the crankshaft 10 and the cylinder sleeve 20), and the flange 50 comprises an upper flange 52 and a lower flange 53, as Figure 8 shown, the distance between the axis of the inner ring of the cylinder sleeve 20 and the axis of the inner ring of the lower flange 53 is e, that is, equal to the eccentricity of the eccentric part 11.

[0101] Optionally, the first assembly gap between the crankshaft 10 and the flange 50 is 0.005mm-0.05mm.

[0102] Preferably, the first assembly gap is 0.01-0.03mm.

[0103] 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.

[0104] 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.

[0105] As Figures 2 to 7 shown, the shaft body part 12 of the crankshaft 10 is integrally formed, and the shaft body part 12 has only one axis. In this way, the shaft body part 12 is formed at one time, thereby reducing the manufacturing difficulty of the shaft body part 12.

[0106] 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.

[0107] Optionally, the first segment and the second segment are detachably connected. In this way, the assembly and disassembly of the crankshaft 10 are facilitated.

[0108] 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.

[0109] 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.

[0110] 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.

[0111] 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.

[0112] Preferably, the first included angle A is 160 degrees, and the second included angle B is 80 degrees.

[0113] Preferably, the first included angle A is 165 degrees, and the second included angle B is 82.5 degrees.

[0114] Preferably, the first included angle A is 170 degrees, and the second included angle B is 85 degrees.

[0115] Preferably, the first included angle A is 175 degrees, and the second included angle B is 87.5 degrees.

[0116] Preferably, the first included angle A is 180 degrees, and the second included angle B is 90 degrees.

[0117] Preferably, the first included angle A is 185 degrees, and the second included angle B is 92.5 degrees.

[0118] Preferably, the first included angle A is 190 degrees, and the second included angle B is 95 degrees.

[0119] Preferably, the first included angle A is 195 degrees, and the second included angle B is 97.5 degrees.

[0120] 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.

[0121] As shown in Figures 2 to 7 , the eccentric portion 11 is cylindrical.

[0122] 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.

[0123] Optionally, the proximal end of the eccentric portion 11 protrudes from the outer circle of the shaft body portion 12 of the crankshaft 10.

[0124] 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.

[0125] It should be noted that in an embodiment of the present application not shown in the figure, the slider 40 comprises a plurality of sub-structures, which are spliced to form a through hole 41.

[0126] 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.

[0127] 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.

[0128] 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.

[0129] As shown in Figure 9 , the projection of the slider 40 in the axial direction of the through hole 41 has two opposite parallel straight line segments and an arc line segment connecting the end portions of the two straight line segments. The limiting channel 31 has a set of oppositely arranged first sliding surfaces in sliding contact with the slider 40, the slider 40 has second sliding surfaces matched with the first sliding surfaces, the slider 40 has an extrusion surface 42 facing the end portion of the limiting channel 31, the extrusion surface 42 serves as the head of the slider 40, the two second sliding surfaces are connected through the extrusion surface 42, and the extrusion surface 42 faces the variable volume cavity 311. In this way, the second sliding surface of the slider 40 in the axial direction of the through hole 41 is a straight line segment, and at the same time, the extrusion surface 42 of the slider 40 in the axial direction of the through hole 41 is an arc line segment.

[0130] Specifically, the extrusion surface 42 is an arc surface, and the distance between the center of the arc surface and the center of the through hole 41 is equal to the eccentricity of the eccentric part 11. Figure 9 In the middle, the center of the through hole 41 of the slider 40 is O. 滑块 The distance between the center of the two arc surfaces and the center of the through hole 41 is 'e', ​​that is, the eccentricity of the eccentric part 11. Figure 9 The dashed X-line in the diagram represents the circle containing the center of the two arc surfaces.

[0131] Optionally, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder liner 20.

[0132] 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.

[0133] Preferably, the difference ranges from -0.02 to 0.02 mm.

[0134] 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.

[0135] Preferably, S 滑块 / S 排 The value is 12 to 18.

[0136] 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.

[0137] Alternatively, the above-mentioned components can be connected by welding, heat fitting, or cold pressing.

[0138] 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 .

[0139] It should be noted that, in the embodiment, the closed space surrounded by the slider 40, the limiting channel 31, the cylinder sleeve 20 and the upper flange 52 (or the lower flange 53) is the variable volume chamber 311, and the pump body assembly 83 has four variable volume chambers 311. In the process of rotating the crankshaft 10, the crankshaft 10 rotates twice, and the single variable volume chamber 311 completes one suction and exhaust process. For the compressor, the crankshaft 10 rotates twice, and a total of four suction and exhaust processes are completed.

[0140] 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.

[0141] As shown in Figures 10 to 15 , in the process of reciprocating movement of the slider 40 in the limiting channel 31, the slider 40 rotates relative to the cylinder sleeve 20, Figures 10 to 12 In the process of rotating the slider 40 clockwise from 0 degrees to 180 degrees, the variable volume chamber 311 increases, and in the process of increasing the variable volume chamber 311, the variable volume chamber 311 is in communication with the suction chamber 23 of the cylinder sleeve 20. When the slider 40 rotates to 180 degrees, the volume of the variable volume chamber 311 reaches the maximum value, and at this time, the variable volume chamber 311 is disconnected from the suction chamber 23, thereby completing the suction operation. Figures 13 to 15 In the process of rotating the slider 40 from 180 degrees to 360 degrees in the clockwise direction, the variable volume chamber 311 decreases, and the slider 40 compresses the gas in the variable volume chamber 311. When the slider 40 rotates to the position where the variable volume chamber 311 is in communication with the compression exhaust port 22, and when the gas in the variable volume chamber 311 reaches the exhaust pressure, the exhaust valve piece 61 of the exhaust valve assembly 60 is opened, and the exhaust operation starts, until the compression ends and enters the next cycle.

[0142] As shown in Figures 10 to 15 , the point marked as M is taken as the reference point of the relative movement between the slider 40 and the crankshaft 10, Figure 11This represents the process of slider 40 rotating clockwise from 0 degrees to 180 degrees. The angle of rotation of slider 40 is θ1, and the corresponding angle of rotation of crankshaft 10 is 2θ1. Figure 13 The diagram shows the process of slider 40 continuing to rotate clockwise from 180 degrees to 360 degrees. The rotation angle of slider 40 is 180° + θ2, and the corresponding rotation angle of crankshaft 10 is 360° + 2θ2. Figure 14 The diagram shows the process of slider 40 continuing to rotate clockwise from 180 degrees to 360 degrees, and the variable volume cavity 311 is connected to the compression exhaust port 22. The angle of rotation of slider 40 is 180°+θ3, and the corresponding angle of rotation of crankshaft 10 is 360°+2θ3. That is, when slider 40 rotates 1 revolution, the corresponding crankshaft 10 rotates 2 revolutions, where θ1 < θ2 < θ3.

[0143] The following is a detailed introduction to the operation of the compressor:

[0144] like Figure 1 As shown, the motor assembly 82 drives the crankshaft 10 to rotate. The two eccentric parts 11 of the crankshaft 10 drive the corresponding two sliders 40 to move. While the sliders 40 revolve around the axis of the crankshaft 10, the sliders 40 rotate relative to the eccentric parts 11. The sliders 40 reciprocate along the limiting channel 31 and drive the cross groove structure 30 to rotate inside the cylinder liner 20. The sliders 40 revolve along the limiting channel 31 while revolving, thus forming the cross slider mechanism motion mode.

[0145] To address the issue of reducing exhaust losses, this application combines venting from the flange 50 end face with venting from the cylinder liner 20 side to reduce compressor exhaust losses, as detailed below:

[0146] like Figures 1 to 27 As shown, at least one of the two flanges 50 has a first axial vent hole 511, and at least one of the two flanges 50 has a second axial vent hole 512; wherein, at least one of the two axial ends of the cylinder liner 20 has a bevel 27 at the edge of the inner circle, the bevel 27 is connected to the first axial vent hole 511, and at least one vent 22 is provided on the side wall of the cylinder liner 20, the vent 22 is connected to the second axial vent hole 512.

[0147] By opening the first axial exhaust hole 511 on at least one of the two flanges 50, and opening the second axial exhaust hole 512 on at least one of the two flanges 50; at the same time, the edge of the inner circle of at least one end of the axial end of the cylinder sleeve 20 has an oblique notch 27, the oblique notch 27 is in communication with the first axial exhaust hole 511, and the side wall surface of the cylinder sleeve 20 has at least one exhaust port 22, which is in communication with the second axial exhaust hole 512. In this way, the exhaust reliability of the fluid machine is ensured, thereby reducing the exhaust loss of the fluid machine, and the efficiency of the fluid machine is improved.

[0148] As shown in Figure 2 and Figure 21 , the first axial exhaust hole 511 and the second axial exhaust hole 512 on the same flange 50 are on the same radius of the flange 50, and the second axial exhaust hole 512 is located on the outer peripheral side of the first axial exhaust hole 511. In this way, it is beneficial to reduce the throttling loss, thereby improving the performance of the compressor, in addition, the design difficulty and the processing and manufacturing difficulty of the flange 50 are reduced, and subsequent abnormal situations are easy to find out the reasons and analyze.

[0149] As shown in Figure 2 and Figure 16 , the flange 50 at one end of the oblique notch 27 of the cylinder sleeve 20 is provided with the first axial exhaust hole 511, and the oblique notch 27 is arranged opposite to the first axial exhaust hole 511. In this way, the exhaust reliability of the variable volume chamber 311 in communication with the oblique notch 27 is ensured.

[0150] Further, the geometric center line of the first axial exhaust hole 511 passes through the geometric center of the oblique notch 27. In this way, it is beneficial to reduce the exhaust loss, thereby ensuring that the efficiency of the compressor can be optimal.

[0151] Optionally, the projection of the sliding block 40 in the sliding direction thereof is a part of a semicircle.

[0152] As shown in Figure 2 , Figure 9 and Figure 17 , the projection of the sliding block 40 in the axial direction of the through hole 41 has two opposite parallel straight line segments and an arc segment connecting the ends of the two straight line segments; the setting position of the exhaust port 22 in the circumferential direction of the cylinder sleeve 20 is within the angle range of (arccos(2R / B)~2×arccos2R / B), wherein R is the inner circle radius of the cylinder sleeve 20, and B is the distance between the two opposite parallel straight line segments of the projection of the sliding block 40 in the axial direction of the through hole 41. In this way, by reasonably optimizing the setting position of the exhaust port 22 in the circumferential direction of the cylinder sleeve 20, it is beneficial to avoid over-compression or under-compression of the compressor, Figure 17The angle range of θ in the formula is (arccos(2R / B)~2×arccos2R / B), that is, the exhaust port 22 can be arranged in the above range in the circumferential direction of the cylinder sleeve 20.

[0153] As shown in Figures 10 to 18 , the cylinder sleeve 20 is provided with an exhaust cavity 25 on the outer wall, and the exhaust port 22 is communicated to the exhaust cavity 25 by the inner wall of the cylinder sleeve 20. The fluid machine further comprises an exhaust valve assembly arranged in the exhaust cavity 25 and corresponding 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.

[0154] As shown in Figures 10 to 18 , the cylinder sleeve 20 is further provided with a communication hole 26 on the axial end face, the communication hole 26 is communicated with the exhaust cavity 25, and the communication hole 26 is communicated with the second axial exhaust hole 512. In this way, the exhaust reliability of the cylinder sleeve 20 is ensured.

[0155] Further, as shown in Figure 2 , 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 connected with the cylinder sleeve 20 and sealing 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.

[0156] Optionally, the exhaust cover plate 70 is fixed on the cylinder sleeve 20 by a fastener.

[0157] Optionally, the fastener is a screw.

[0158] Optionally, the outer contour of the exhaust cover plate 70 is matched with the outer contour of the exhaust cavity 25.

[0159] As shown in Figure 18 , the distance between the plane where the one end of the exhaust port 22 communicated with the exhaust cavity 25 is located and the axis of the cylinder sleeve 20 is K, and the inner circle radius of the cylinder sleeve 20 is R, wherein 1mm≦K-R≦5mm. In this way, by reasonably optimizing the value range of K-R, the reliability requirements of the compressor are met. On the one hand, it avoids that the thinner the thickness of the cylinder sleeve wall at the exhaust port 22 is, the less the strength of the cylinder sleeve wall at the exhaust port 22 is, which leads to the fracture of the cylinder sleeve wall at the exhaust port 22 caused by the high-frequency impact of the valve plate in the subsequent exhaust valve assembly; on the other hand, it also avoids that the thickness of the cylinder sleeve wall at the exhaust port 22 is too thick, although the strength of the cylinder sleeve wall at the exhaust port 22 can meet the requirements, but the clearance volume is increased, which leads to the increase of the energy efficiency reduction of the compressor.

[0160] As shown in Figure 23 and Figure 24As shown, the cross-sectional area of ​​the exhaust chamber 25 along the axial direction of the cylinder liner 20 is S3, the height of the exhaust chamber 25 along the axial direction of the cylinder liner 20 is N, and the displacement of the fluid machinery is V, where 0.2≦(N×S3) / V≦5. Thus, by reasonably optimizing the ratio range of the exhaust chamber 25 volume to the compressor (fluid machinery) displacement V, it is ensured that the exhaust chamber 25 can reduce exhaust noise and reduce the oil circulation rate during high-speed compressor operation. Here, S3 is in square millimeters, and N is in mm.

[0161] It should be noted that, in this embodiment, another optional embodiment may also be provided, such as... Figure 25 and Figure 26 As shown, an exhaust chamber 25 is provided on the outer wall of the cylinder liner 20. A boss structure 29 is provided on the cavity wall of the exhaust chamber 25. The exhaust port 22 extends from the inner wall of the cylinder liner 20 to the boss structure 29 and communicates with the exhaust chamber 25. In this way, the boss structure 29 is an outwardly convex structure. By providing the boss structure 29, it is beneficial to reduce the opening loss of the exhaust valve plate of the exhaust valve assembly due to the stickiness of lubricating oil.

[0162] Furthermore, such as Figure 26 As shown, the thickness of the boss structure 29 in the extension direction of the exhaust port 22 is M, where 0.05mm≦M≦3mm. In this way, on the one hand, the cylinder liner wall thickness at the exhaust port 22 is increased to ensure that the cylinder liner wall at this location has sufficient strength; on the other hand, the opening loss of the exhaust valve plate of the exhaust valve assembly can also be reduced.

[0163] It should be noted that, in this application, if Figure 27 As shown, the cross-sectional area of ​​the slider 40 in its sliding direction is S, as follows. Figure 22 As shown, the assembly eccentricity of the cross-slot structure 30 is e. According to the compressor operating principle, the volume of a single variable volume chamber 311 is V1 = 4eS, the working volume of the entire compressor is V, and V = 4V1 = 16eS. That is, the displacement of the compressor is 16eS, in cubic millimeters.

[0164] It should be noted that, in this application, if Figure 23 and Figure 41 As shown, the cross-sectional area of ​​the exhaust port 22 is S1, and the volume of a single variable volume cavity 311 is V1, where 750≦V1 / S1≦3300. Thus, by reasonably optimizing the ratio range of the volume V1 of a single variable volume cavity 311 to the cross-sectional area S1 of the exhaust port 22, the cross-sectional area S1 of the exhaust port 22 is ensured to be within a reasonable range. This avoids a large exhaust velocity due to an excessively small exhaust port 22, leading to increased exhaust losses, and conversely, avoids a large clearance volume due to an excessively large exhaust port 22 (see [reference]). Figure 41), wherein the unit of V1 is cubic millimeter, and the unit of S1 is square millimeter.

[0165] It should be noted that, Figure 41 The COP in the formula (1) refers to the ratio of the refrigerating or heating capacity of the compressor to the power consumption of the compressor, which is a parameter reflecting the performance and energy saving of the compressor.

[0166] It should be noted that in the present application, the value range of the ratio V1 / S1 is the ratio of numerical values, without unit.

[0167] As shown in Figure 2 and Figure 19 , the longitudinal section of the chamfered cutout 27 through the diameter of the cylinder sleeve 20 coincides with the longitudinal section of the exhaust port 22 through the diameter of the cylinder sleeve 20, and specifically, as shown in Figure 19 , the figure shows that the setting position of the chamfered cutout 27 in the circumferential direction of the cylinder sleeve 20 is within the angle range of (arccos(2R / B)~2×arccos2R / B), wherein R is the inner radius of the cylinder sleeve 20, and B is the distance between the two opposite parallel straight line segments of the projection of the sliding block 40 in the axial direction of the through hole 41. In this way, by reasonably optimizing the setting position of the chamfered cutout 27 in the circumferential direction of the cylinder sleeve 20, it is beneficial to avoid over-compression or under-compression of the compressor, Figure 19 , the angle range of β is (arccos(2R / B)~2×arccos2R / B), that is, the chamfered cutout 27 can be set within the above range in the circumferential direction of the cylinder sleeve 20.

[0168] As shown in Figure 20 , the inclination direction of the chamfered cutout 27 is from the end face of one end of the cylinder sleeve 20 to extend close to the axis of the cylinder sleeve 20, and the included angle between the chamfered cutout 27 and the end face of the cylinder sleeve 20 is α, wherein 15°≦α≦60°. In this way, it is beneficial to reduce the exhaust loss, thereby improving the performance of the compressor, in addition, the chamfered cutout 27 can play a role in guiding the airflow, but the chamfered cutout 27 will increase the clearance of the compressor, so that the performance of the compressor is reduced. Since the flow of gas has resistance and loss, by reasonably optimizing the included angle α between the chamfered cutout 27 and the end face of the cylinder sleeve 20, the optimal point between the gas flow loss and the increased clearance can be found.

[0169] As shown in Figure 20 , the equivalent diameter of the circle where the chamfered cutout 27 is located is D, and the volume of a single variable volume chamber 311 is V1, wherein 400≦V1 / D≦1000, wherein the unit of D is mm. In this way, it is beneficial to reduce the exhaust noise as much as possible, by reasonably optimizing the equivalent diameter D of the circle where the chamfered cutout 27 is located, the ratio of V1 / D can satisfy: 400≦V1 / D≦1000, and the optimal point between the gas flow loss and the increased clearance can be found.

[0170] It should be noted that in the present application, the value range of the ratio V1 / D is the ratio of numerical values, without units.

[0171] As shown in Figure 21 , the cross-sectional area of the hole section of the first axial exhaust port 22 is S4, and the volume of the single variable volume chamber 311 is V1, wherein 750≦V1 / S4≦3300. In this way, the balance between the exhaust loss and the clearance volume is taken into account, and the COP of the compressor can be ensured to be optimal.

[0172] It should be noted that in the present application, the value range of the ratio V1 / S4 is the ratio of numerical values, without units.

[0173] As shown in Figure 21 , the cross-sectional area of the hole section of the second axial exhaust port 22 is S2, and the volume of the single variable volume chamber 311 is V1, wherein 50≦V1 / S2≦250. In this way, the balance between the exhaust loss and the clearance volume is taken into account, and the COP of the compressor can be ensured to be optimal.

[0174] It should be noted that in the present application, the value range of the ratio V1 / S2 is the ratio of numerical values, without units.

[0175] As shown in Figure 2 , Figures 10 to 20 , Figure 22 and Figure 24 , the cylinder sleeve 20 has a radial suction hole 21 and a suction chamber 23, and the suction chamber 23 communicates with the radial suction hole 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.

[0176] Optionally, the suction chamber 23 is a cavity formed by hollowing out the inner wall of the cylinder sleeve 20 in the radial direction, and the suction chamber 23 can be one or two above and below.

[0177] Specifically, the suction chamber 23 extends a first predetermined distance around the circumference of the inner wall 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.

[0178] As shown in Figure 2 , Figures 10 to 20 , Figure 22 and Figure 24As shown, the suction cavities 23 are two, the two suction cavities 23 are arranged axially spaced apart along the cylinder sleeve 20, the cylinder sleeve 20 further has a suction communication cavity 24, the two suction cavities 23 are communicated with the suction communication cavity 24, and the radial suction hole 21 is communicated with the suction cavity 23 through the suction communication cavity 24. In this way, it is beneficial to increase the volume of the suction cavity 23, thereby reducing the suction pressure pulsation.

[0179] Further, as shown in the drawings, Figure 2 the suction communication cavity 24 extends along the axial direction of the cylinder sleeve 20 by a second predetermined 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, it is convenient to open the suction communication cavity 24 from the end surface of the cylinder sleeve 20, and the machining convenience of the suction communication cavity 24 is ensured.

[0180] It should be noted that in the present embodiment, as shown in the drawings, Figure 2 the cylinder sleeve 20 is provided with an exhaust port 22 on the side wall close to the lower flange 53, and a bevel cutout 27 is opened on the inner circle of the end of the cylinder sleeve 20 towards the upper flange 52, and the upper flange 52 is provided with a first axial exhaust hole 511 and a second axial exhaust hole 512, wherein the exhaust port 22 is communicated with the second axial exhaust hole 512 through an exhaust cavity 25 and a communication hole 26, and the bevel cutout 27 is communicated with the first axial exhaust hole 511.

[0181] Embodiment two

[0182] It should be noted that the difference between the present embodiment and embodiment one is that, as shown in the drawings, Figure 28 the cylinder sleeve 20 is provided with an exhaust port 22 on the side wall close to the upper flange 52, and a bevel cutout 27 is opened on the inner circle of the end of the cylinder sleeve 20 towards the lower flange 53, and the lower flange 53 is provided with a first axial exhaust hole 511, and the upper flange 52 is provided with a second axial exhaust hole 512, wherein the exhaust port 22 is communicated with the second axial exhaust hole 512 through an exhaust cavity 25 and a communication hole 26, and the bevel cutout 27 is communicated with the first axial exhaust hole 511.

[0183] Embodiment three

[0184] It should be noted that the difference between the present embodiment and embodiment one is that, as shown in the drawings, Figure 29 the cylinder sleeve 20 is provided with an exhaust port 22 on the side wall close to the upper flange 52, and a bevel cutout 27 is opened on the inner circle of the end of the cylinder sleeve 20 towards the lower flange 53, and the lower flange 53 is provided with a first axial exhaust hole 511 and a second axial exhaust hole 512, wherein the exhaust port 22 is communicated with the second axial exhaust hole 512 through an exhaust cavity 25 and a communication hole 26, and the bevel cutout 27 is communicated with the first axial exhaust hole 511.

[0185] Embodiment four

[0186] It should be noted that the difference between the present embodiment and embodiment one is that, asFigure 30 As shown in the figure, the side wall of the cylinder sleeve 20 near the upper flange 52 is provided with an exhaust port 22, and the inner circle of the end of the cylinder sleeve 20 towards the upper flange 52 is provided with a bevel cut 27. The side wall of the cylinder sleeve 20 near the lower flange 53 is provided with an exhaust port 22, and the inner circle of the end of the cylinder sleeve 20 towards the lower flange 53 is provided with a bevel cut 27. The upper flange 52 and the lower flange 53 are both provided with a first axial exhaust hole 511 and a second axial exhaust hole 512. The exhaust port 22 on the upper side of the cylinder sleeve 20 is communicated with the second axial exhaust hole 512 on the upper flange 52 through the exhaust cavity 25 and the communication hole 26, and the bevel cut 27 on the upper end surface of the cylinder sleeve 20 is communicated with the first axial exhaust hole 511 on the upper flange 52. The exhaust port 22 on the lower side of the cylinder sleeve 20 is communicated with the second axial exhaust hole 512 on the lower flange 53 through the exhaust cavity 25 and the communication hole 26, and the bevel cut 27 on the lower end surface of the cylinder sleeve 20 is communicated with the first axial exhaust hole 511 on the lower flange 53.

[0187] Example five

[0188] It should be noted that the difference between this embodiment and example one is that, as shown in the figure, the cylinder sleeve 20 is provided with two radial air inlet holes 21, and the two radial air inlet holes 21 are arranged in the axial direction of the cylinder sleeve 20 and are communicated with the corresponding air inlet cavities 23. Figure 31

[0189] Example six

[0190] It should be noted that the difference between this embodiment and example two is that, as shown in the figure, the cylinder sleeve 20 is provided with two radial air inlet holes 21, and the two radial air inlet holes 21 are arranged in the axial direction of the cylinder sleeve 20 and are communicated with the corresponding air inlet cavities 23. Figure 32

[0191] Example seven

[0192] It should be noted that the difference between this embodiment and example three is that, as shown in the figure, the cylinder sleeve 20 is provided with two radial air inlet holes 21, and the two radial air inlet holes 21 are arranged in the axial direction of the cylinder sleeve 20 and are communicated with the corresponding air inlet cavities 23. Figure 33

[0193] Example eight

[0194] It should be noted that the difference between this embodiment and example four is that, as shown in the figure, the cylinder sleeve 20 is provided with two radial air inlet holes 21, and the two radial air inlet holes 21 are arranged in the axial direction of the cylinder sleeve 20 and are communicated with the corresponding air inlet cavities 23. Figure 34

[0195] ​​​​Of course, in one embodiment not shown in the drawings, the upper flange 52 and the lower flange 53 can be used for suction, or one of the two flanges 50 can be used for suction in combination with the cylinder liner 20.

[0196] It is to be understood that the terminology used herein is for the purpose of describing particular 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.

[0197] The relative arrangement of parts and steps, numerical expressions, and numerical values set forth in the examples are not intended to limit the scope of the application, unless otherwise specifically stated. It is to be understood that the drawings are not necessarily to scale as the dimensions of the parts shown are for the purpose of illustration and description only. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art can not be discussed in detail, but are to be considered as part of the description of the application. In all examples shown and discussed herein, any specific values are to be interpreted as illustrative only and not as a limitation. Thus, other examples of example embodiments can have different values. It is noted that like numbers and letters on the figures identify like parts throughout the disclosure, and thus, once defined, no further discussion of such parts is necessary.

[0198] For the purposes of this description, spatially relative terms such as "above", "below", "up", "down", "top", "bottom", "side" and the like, are intended to describe the relative position of one element to another element as shown in the drawings. Such relative terms do not necessarily indicate the orientation of the device in use or during operation. For example, if the device is turned over, then the element described as above other elements would now be below the other elements. Accordingly, the exemplary term "above" can encompass both an orientation of above and below. The device can be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

[0199] It is to be understood that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting, as the scope of the exemplary embodiments of this application is limited only by the appended claims. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. Also, unless otherwise indicated herein, the materials described herein can be used in a variety of applications.

[0200] It should be noted that the terms "first", "second", and the like, as used in the description and the claims herein are intended to modify a particular disclosed embodiment unless otherwise indicated, but do not imply that the architecture having such designation must be the first or second among its field or order of importance. It is also to be understood that the use of the terms "first", "second", etc., was merely used to parameterize similar objects to distinguish one from another without necessarily implying that one came before or after the other.

[0201] The preferred embodiments of the application are described above in detail. The application, however, is not limited to the precise embodiments described, and obviously many modifications and changes can be made by those skilled in the art without departing from the spirit and scope of the application. It is intended that all such modifications and changes be included within the scope of the application as described in the foregoing description and as pointed out in the claims.

Claims

1. A fluid machine characterized by, Comprising: a crankshaft (10) provided with two eccentric portions (11) along its axial direction; a cylinder sleeve (20) eccentrically provided with the crankshaft (10) and with a fixed eccentric distance; a cross groove structure (30) rotatably provided in the cylinder sleeve (20), the cross groove structure (30) having two limiting channels (31) sequentially provided along the axial direction of the crankshaft (10), the extending direction of the limiting channels (31) being perpendicular to the axial direction of the crankshaft (10); two sliders (40) having through holes (41), the two eccentric portions (11) corresponding to extend into the two through holes (41) of the two sliders (40), the two sliders (40) corresponding to be slidingly provided in the two limiting channels (31) and forming a variable volume cavity (311) in the sliding direction of the sliders (40), the crankshaft (10) rotating to drive the sliders (40) to reciprocatingly slide in the limiting channels (31) while interacting with the cross groove structure (30), so that the cross groove structure (30) and the sliders (40) rotate in the cylinder sleeve (20); two flanges (50) provided at the two axial ends of the cylinder sleeve (20), at least one of the two flanges (50) being provided with a first axial exhaust hole (511), and at least one of the two flanges (50) being provided with a second axial exhaust hole (512); wherein, the edge of the inner circle of at least one of the two axial ends of the cylinder sleeve (20) has an oblique notch (27), the oblique notch (27) being in communication with the first axial exhaust hole (511), and the side wall surface of the cylinder sleeve (20) has at least one exhaust port (22), the exhaust port (22) being in communication with the second axial exhaust hole (512); the first axial exhaust hole (511) and the second axial exhaust hole (512) on the same flange (50) are on the same radius of the flange (50), and the second axial exhaust hole (512) is located on the outer peripheral side of the first axial exhaust hole (511); the inclination direction of the oblique notch (27) is along the axial end surface of the cylinder sleeve (20) to extend towards the axis of the cylinder sleeve (20), and the included angle between the oblique notch (27) and the end surface of the cylinder sleeve (20) is α, wherein 15°≦α≦60°.

2. The fluid machine of claim 1, wherein, the flange (50) at one end of the oblique notch (27) of the cylinder sleeve (20) is provided with the first axial exhaust hole (511), and the oblique notch (27) and the first axial exhaust hole (511) are oppositely arranged.

3. The fluid machine of claim 2, wherein, the geometric center line of the first axial exhaust hole (511) passes through the geometric center of the oblique notch (27).

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

5. The fluid machine according to claim 1, wherein An exhaust cavity (25) is formed in the outer wall of the cylinder sleeve (20), 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 which is arranged in the exhaust cavity (25) and corresponds to the exhaust port (22); A communication hole (26) is further arranged on the axial end surface of the cylinder sleeve (20), the communication hole (26) is communicated with the exhaust cavity (25), and the communication hole (26) is communicated with the second axial exhaust hole (512).

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

7. The fluid machine of claim 5, wherein, The cavity sectional area of the exhaust cavity (25) in the axial direction of the cylinder sleeve (20) is S3, the height of the exhaust cavity (25) in the axial direction of the cylinder sleeve (20) is N, and the displacement of the fluid machine is V, wherein 0.2≦(N×S3) / V≦5.

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

9. The fluid machine of claim 8, wherein, The thickness of the boss structure (29) in the extension direction of the exhaust port (22) is M, wherein 0.05mm≦M≦3mm.

10. The fluid machine of claim 1, wherein, The sectional area of the hole section of the exhaust port (22) is S1, and the volume of a single variable volume chamber (311) is V1, wherein 750≦V1 / S1≦3300.

11. The fluid machine of claim 1, wherein, The equivalent diameter of the circle where the bevel cut (27) is located is D, and the volume of a single variable volume chamber (311) is V1, wherein 400≦V1 / D≦1000.

12. The fluid machine of claim 1, wherein, The longitudinal section of the diameter of the cylinder sleeve (20) through the bevel cut (27) coincides with the longitudinal section of the diameter of the cylinder sleeve (20) through the exhaust port (22).

13. The fluid machine according to claim 1, wherein The sectional area of the hole section of the first axial exhaust port (22) is S4, and the volume of a single variable volume chamber (311) is V1, wherein 750≦V1 / S4≦3300; and / or, A cross-sectional area of a hole section of the second axial exhaust port (22) is S2, and a volume of a single variable volume chamber (311) is V1, wherein 50≦V1 / S2≦250.

14. The fluid machine of claim 5, wherein, The exhaust cavity (25) penetrates to an 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).

15. The fluid machine of any one of claims 1 to 14, wherein, The two eccentric portions (11) have a phase difference with a first included angle A, the eccentric amounts of the two eccentric portions (11) are equal, and the extension directions of the two limit channels (31) have a phase difference with a second included angle B, wherein the first included angle A is twice the second included angle B.

16. 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 15.

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