Fluid machine and heat exchange device

Abstract

The application provides a fluid machine and a heat exchange device, and the fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure and a sliding block, the crankshaft is provided with two eccentric parts along the axial direction of the crankshaft; the crankshaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve, two limiting channels of the cross groove structure are sequentially arranged along the axial direction of the crankshaft, and the extension direction of the limiting channel is perpendicular to the axial direction of the crankshaft; the two eccentric parts correspondingly extend into two through holes of the two sliding blocks; wherein the cylinder sleeve is provided with at least one radial air inlet hole, the radial air inlet hole is used for being communicated with a variable volume cavity, and the ratio S / V of the sectional area S of the hole section of a single radial air inlet hole to the displacement V of the fluid machine ranges from 0.006 to 0.01. The application solves the problems of low energy efficiency, large noise and insufficient air suction of the fluid machine 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 fluid machines and expanders, etc. Taking the fluid machine 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 fluid machine 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 type fluid machine as the mainstream fluid machine of household air conditioners 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 fluid machine with high energy efficiency, low noise and other characteristics.

[0004] In addition, the existing fluid machine has the phenomenon of insufficient suction, and the suction loss increases due to insufficient suction. 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 fluid machine in the prior art and how to solve the problem of insufficient suction of the fluid machine.

[0006] In order to achieve the above purpose, according to one aspect of the present application, a fluid machine is provided, comprising a crankshaft, a cylinder sleeve, a cross groove structure and a sliding block, the crankshaft is provided with two eccentric parts along its axial direction; the crankshaft is eccentrically arranged with the cylinder sleeve and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve, the cross groove structure has two limiting channels, the two limiting channels are sequentially arranged along the axial direction of the crankshaft, and the extension direction of the limiting channel is perpendicular to the axial direction of the crankshaft; the sliding block has a through hole, and there are two sliding blocks, the two eccentric parts correspondingly extend into the two through holes of the two sliding blocks, the two sliding blocks are correspondingly arranged in the two limiting channels and form a variable volume chamber, the variable volume chamber is located in the sliding direction of the sliding block, and the crankshaft rotates to drive the sliding block to reciprocally slide in the limiting channel while interacting with the cross groove structure, so that the cross groove structure and the sliding block rotate in the cylinder sleeve; wherein the cylinder sleeve has at least one radial suction hole, the radial suction hole is used for communication with the variable volume chamber, and the ratio S / V of the cross-sectional area S of the single radial suction hole to the displacement V of the fluid machine is in the range of 0.006-0.01.

[0007] Further, the inner wall surface of the cylinder sleeve has a suction chamber, and the radial suction hole communicates with the variable volume chamber through the suction chamber.

[0008] Further, the suction chamber extends a first preset distance around the circumference of the inner wall surface of the cylinder sleeve to form an arc-shaped suction chamber.

[0009] Further, the two suction cavities are arranged along the axial direction of the cylinder sleeve and are spaced apart, the cylinder sleeve further has a suction communication cavity, and the two suction cavities are in communication with the suction communication cavity.

[0010] Further, the suction communication cavity extends along the axial direction of the cylinder sleeve by a second preset distance, and at least one end of the suction communication cavity penetrates the axial end surface of the cylinder sleeve.

[0011] Further, the radial suction hole is symmetrical about the center line between the two end surfaces in the axial direction of the cylinder sleeve; the two suction cavities are symmetrical about the center line between the two end surfaces in the axial direction of the cylinder sleeve; the suction communication cavity comprises two sub-suction communication cavities in communication, and the two sub-suction communication cavities are symmetrical about the center line between the two end surfaces in the axial direction of the cylinder sleeve.

[0012] Further, the radial suction hole is asymmetrical about the center line between the two end surfaces in the axial direction of the cylinder sleeve; the two suction cavities are asymmetrical about the center line between the two end surfaces in the axial direction of the cylinder sleeve; the suction communication cavity comprises two sub-suction communication cavities in communication, and the two sub-suction communication cavities are asymmetrical about the center line between the two end surfaces in the axial direction of the cylinder sleeve.

[0013] Further, with the center line between the two end surfaces in the axial direction of the cylinder sleeve as a reference, the diameter of the cavity section of the sub-suction communication cavity on the side close to the axis of the radial suction hole is d1, and the diameter of the cavity section of the sub-suction communication cavity on the side away from the axis of the radial suction hole is d2, wherein d1

[0014] Further, the two suction cavities are arranged along the axial direction of the cylinder sleeve and are spaced apart, and the two radial suction holes correspond to the two suction cavities one by one and are in communication with the corresponding variable-volume cavities through the two suction cavities.

[0015] Further, the fluid machine further comprises two flanges, the two flanges are arranged at the two axial ends of the cylinder sleeve respectively, and the exhaust passages are arranged on the end surfaces of the two flanges and are in communication with the corresponding variable-volume cavities.

[0016] Further, the end of the radial suction hole is a compressed intake port, and the initial end of the exhaust passage is a compressed exhaust port, when any one of the sliding blocks is in the intake position, the compressed intake port is in communication with the corresponding variable-volume cavity; when any one of the sliding blocks is in the exhaust position, the corresponding variable-volume cavity is in communication with the compressed exhaust port.

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

[0018] Further, the end of the radial suction hole is an expansion exhaust port, and the initial end of the exhaust passage is an expansion intake port, the expansion exhaust port is communicated with the variable volume chamber on the corresponding side when any one of the sliders is in the intake position, and the variable volume chamber on the corresponding side is communicated with the expansion intake port when any one of the sliders is in the exhaust position.

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

[0020] Further, the outer wall of the cylinder sleeve is provided with an exhaust cavity, the cylinder sleeve is further provided with an exhaust port, the exhaust port is communicated with the exhaust cavity through the inner wall of the cylinder sleeve, and the fluid machine further comprises an exhaust valve assembly arranged in the exhaust cavity and corresponding to the exhaust port.

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

[0022] Further, the exhaust cavity is one, and the at least one axial end surface of the cylinder sleeve is further provided with a communication hole, the communication hole is communicated with the exhaust cavity, and the fluid machine further comprises two flanges, the two flanges are arranged at the axial two ends of the cylinder sleeve, and the flange opposite to the communication hole in the two flanges is provided with an exhaust passage, and the communication hole is communicated with the exhaust passage.

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

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

[0025] Further, the two exhaust cavities are not communicated, the two axial end surfaces of the cylinder sleeve are both provided with a communication hole, the two communication holes are respectively communicated with the two exhaust cavities, the fluid machine further comprises two flanges, the two flanges are arranged at the axial two ends of the cylinder sleeve, and the exhaust passage is arranged at the position opposite to the communication hole in the two flanges, and the communication hole is communicated with the exhaust passage.

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

[0027] Further, the exhaust chamber penetrates to the outer wall surface of the cylinder sleeve, and the fluid machine further comprises an exhaust cover plate, the exhaust cover plate is connected with the cylinder sleeve and seals the exhaust chamber.

[0028] Further, the end of the radial suction hole is a compression intake port, and the exhaust port on the cylinder sleeve is a compression exhaust port; when any slider is in the intake position, the compression intake port is communicated with the variable volume chamber of the corresponding side; when any slider is in the exhaust position, the variable volume chamber of the corresponding side is communicated with the compression exhaust port.

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

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

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

[0032] Further, the two eccentric parts have a phase difference of a first included angle A, the eccentricities of the two eccentric parts are equal, and the extension directions of the two limiting channels have a phase difference of a second included angle B, wherein the first included angle A is twice the second included angle B.

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

[0034] By reasonably optimizing the ratio S / V of the sectional area S of the radial suction hole of the cylinder sleeve to the displacement V of the fluid machine in the range of 0.006-0.01, the application avoids the suction loss of the fluid machine due to insufficient suction, so as to ensure that the volumetric efficiency of the fluid machine can reach the optimum in this range. BRIEF DESCRIPTION OF DRAWINGS

[0035] The drawings constituting a part of the specification of the present application are used to provide further understanding of the present application, the schematic embodiments of the present application and the description thereof are used to explain the present application, and do not constitute improper limitation on the present application. In the drawings:

[0036] Figure 1 Fig. 1 shows a schematic diagram of the internal structure of a fluid machine according to an embodiment of the present application;

[0037] Figure 2 Fig. 2 shows a schematic diagram of the structure of a pump body assembly of the fluid machine in Fig. 1; Figure 1

[0038] Figure 3 Fig. 3 shows a schematic diagram of the exploded structure of the pump body assembly in Fig. 2; Figure 2

[0039] Figure 4 Fig. 4 shows a schematic diagram of the assembly structure of the crankshaft, cross groove structure, and slider in Fig. 1; Figure 3

[0040] Figure 5 Fig. 5 shows a schematic diagram of the cross-sectional structure of the crankshaft, cross groove structure, and slider in Fig. 1; Figure 4

[0041] Figure 6 Fig. 6 shows a schematic diagram of the eccentricity of the shaft body portion and the two eccentric portions of the crankshaft in Fig. 1; Figure 3

[0042] Figure 7 Fig. 7 shows a schematic diagram of the cross-sectional structure of the assembly eccentricity of the crankshaft and cylinder sleeve in Fig. 1; Figure 3

[0043] Figure 8 Fig. 8 shows a schematic diagram of the eccentricity between the cylinder sleeve and the lower flange in Fig. 1; Figure 3

[0044] Figure 9 Fig. 9 shows a schematic diagram of the structure of the slider in Fig. 1 in the axial direction of the through hole; Figure 3

[0045] Figure 10 Fig. 10 shows a schematic diagram of the cross-sectional structure of the cylinder sleeve symmetrical suction of the pump body assembly of the fluid machine in Fig. 1; Figure 2

[0046] Figure 11 Fig. 11 shows a schematic diagram of the suction path of the cylinder sleeve in Fig. 1; Figure 10

[0047] Figure 12 Fig. 12 shows a schematic diagram of the cross-sectional structure of the C-C view in Fig. 1; Figure 10

[0048] Figure 13 Fig. 13 shows a schematic diagram of the cross-sectional structure of the D-D view in Fig. 1; Figure 10

[0049] Figure 14 Fig. 14 shows a schematic diagram of the cross-sectional structure of the E-E view in Fig. 1;​​​​​​​​​​​​Figure 2 Fig. 1 shows a structural schematic view of the cylinder liner in the fluid machine of Fig. 1 from a first perspective;

[0050] Figure 15 Fig. 2 shows a structural schematic view of the cylinder liner in Fig. 1 from a second perspective; Figure 14

[0051] Figure 16 Fig. 3 shows a structural schematic view of the cylinder liner in Fig. 1 from a third perspective; Figure 14

[0052] Figure 17 Fig. 4 shows a structural schematic view of the cylinder liner in Fig. 1 from a F-F perspective; Figure 16

[0053] Figure 18 Fig. 5 shows a structural schematic view of the cylinder liner in Fig. 1 from a perspective of a symmetric suction path; Figure 17

[0054] Figure 19 Fig. 6 shows a structural schematic view of the fluid machine according to embodiment two of the present application;

[0055] Figure 20 Fig. 7 shows a structural schematic view of the pump body assembly of the fluid machine in Fig. 1, in which the cylinder liner is asymmetrically suctioned; Figure 19

[0056] Figure 21 Fig. 8 shows a structural schematic view of the cylinder liner according to an alternative embodiment of the present application;

[0057] Figure 22 Fig. 9 shows a sectional structural schematic view of the cylinder liner in Fig. 1 from a G-G perspective; Figure 21

[0058] Figure 23 Fig. 10 shows a structural schematic view of the cylinder liner in Fig. 1 from a perspective of an asymmetric suction path; Figure 22

[0059] Figure 24 Fig. 11 shows a structural schematic view of the cylinder liner in Fig. 1; Figure 19

[0060] Figure 25 Fig. 12 shows a structural schematic view of the cylinder liner in Fig. 1 from a top perspective; Figure 24

[0061] Figure 26 Fig. 13 shows a structural schematic view of the cylinder liner in Fig. 1 from a bottom perspective; Figure 24

[0062] Figure 27 Fig. 14 shows a structural schematic view of the fluid machine according to embodiment three of the present application;

[0063] Figure 28 Fig. 15 shows a structural schematic view of the fluid machine in Fig. 1;​​​​​​​​​​Figure 27 Structural diagram of the pump body assembly of the fluid machine in

[0064] Figure 29 Structural diagram of the cylinder liner according to an alternative embodiment of the present application is shown;

[0065] Figure 30 Structural diagram of the cylinder liner from another perspective in Figure 29

[0066] Figure 31 Structural diagram of the cylinder liner from the top perspective in Figure 29

[0067] Figure 32 Structural diagram of the H-H perspective section of the cylinder liner in Figure 31

[0068] Figure 33 Structural diagram of the suction path of the cylinder liner symmetric double suction in Figure 32

[0069] Figure 34 Structural diagram of the exhaust of the pump body assembly of the fluid machine according to an alternative embodiment of the present application is shown;

[0070] Figure 35 Structural diagram of the upper flange and the lower flange of the pump body assembly in Figure 34

[0071] Figure 36 Structural diagram of the cylinder liner of the pump body assembly in Figure 34

[0072] Structural diagram of the exhaust of the pump body assembly of the fluid machine according to another alternative embodiment of the present application is shown; Figure 37

[0073] Structural diagram of the upper flange of the pump body assembly in Figure 38 Figure 37

[0074] Structural diagram of the cylinder liner of the pump body assembly in Figure 39 Figure 37 Structural diagram of the cylinder liner of the pump body assembly in

[0075] Figure 40 Mechanism principle diagram of the fluid machine operation according to an alternative embodiment of the present application is shown;

[0076] Figure 41 Mechanism principle diagram of the fluid machine operation in Figure 40

[0077] Mechanism principle diagram of the fluid machine operation in​​​​​​​Figure 42 Fig. 1 shows a schematic diagram of the mechanism principle of the fluid machine operation in the prior art;

[0078] Figure 43 Fig. 2 shows a schematic diagram of the mechanism principle of the fluid machine operation in the prior art;

[0079] Figure 44 Fig. 3 shows a schematic diagram of the mechanism principle of the fluid machine operation in the prior art, in which a force arm of the driving shaft driving the slider rotation is shown; Figure 43

[0080] Figure 45 Fig. 4 shows a schematic diagram of the mechanism principle of the fluid machine operation in the prior art, in which the center of the limiting groove structure and the center of the eccentric part coincide; Figure 43

[0081] Figure 46 Fig. 5 shows the influence of the ratio of the sectional area S of the hole section of the radial suction hole to the displacement V of the fluid machine on the volumetric efficiency of the fluid machine.

[0082] In the above drawings, the following reference signs are used:

[0083] 10, crankshaft; 11, eccentric part; 12, shaft body part;

[0084] 20, cylinder sleeve; 21, radial suction hole; 22, exhaust port; 23, suction cavity; 24, suction communication cavity; 25, exhaust cavity; 26, communication hole; 27, bevel cut; 28, exhaust communication port;

[0085] 30, cross groove structure; 31, limiting channel; 311, variable volume cavity; 32, center hole;

[0086] 40, slider; 41, through hole; 42, extrusion surface;

[0087] 50, flange; 51, exhaust channel; 511, first exhaust channel; 512, second exhaust channel; 52, upper flange; 53, lower flange;

[0088] 60, exhaust valve assembly;

[0089] 70, exhaust cover plate;

[0090] 80, distributor component; 81, shell assembly; 82, motor assembly; 83, pump body assembly; 84, upper cover assembly; 85, lower cover assembly;

[0091] 90, fastener. DETAILED DESCRIPTION

[0092] ​​Clearly, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. The following description of at least one example embodiment is merely illustrative in nature and not intended to limit the present application and its applications or uses in any way. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative efforts fall within the scope of the present application.

[0093] As shown in the prior art, Figure 42 A fluid mechanical 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.

[0094] 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.

[0095] 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 fluid machine. Based on the above operating mechanism principle, as shown in Figure 43 A motion mechanism is proposed with O0 as the center of the driving shaft, 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.

[0096] A set of operating mechanisms are correspondingly 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 rotates the limiting groove structure.

[0097] However, as shown in Figure 44As shown, the length of the force arm L driving the slider to rotate is L = 2e x cos theta x cos theta, wherein e is the eccentricity of the eccentric part, and theta is the included angle between the line O1O0 and the sliding direction of the slider in the limiting groove.

[0098] As shown, when the center O1 of the cylinder (i.e., the center of the limiting groove structure) coincides with the center of the eccentric part, the resultant force of the driving force of the driving shaft passes through the center of the limiting groove structure, i.e., the torque applied to the limiting groove structure is zero, and the limiting groove structure cannot rotate, at this time, the movement mechanism is in the dead point position and cannot drive the slider to rotate. Figure 45

[0099] 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 fluid machine is constructed based on the principle, which has the characteristics of high energy efficiency and low noise, and below, the fluid machine is taken as an example to specifically introduce the fluid machine based on the cross groove structure with two limiting channels and double sliders.

[0100] In order to solve the problems of low energy efficiency and large noise of the fluid machine in the prior art, the application provides a fluid machine and a heat exchange equipment, wherein the heat exchange equipment comprises the above and the following fluid machine.

[0101] 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 thereof, the two eccentric parts 11 have a phase difference of a first included angle A, and the eccentricities 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, 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 reciprocate in the limiting channel 31, the slider 40 interacts with the cross groove structure 30, so that the cross groove structure 30 and the slider 40 rotate in the cylinder sleeve 20.

[0102] ​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.

[0103] In addition, the fluid machine provided by the present application can operate stably, that is, the energy efficiency of the fluid machine is higher and the noise is smaller, thereby ensuring the working reliability of the heat exchange equipment.

[0104] It should be noted that in the present application, the first included angle A and the second included angle B are not zero.

[0105] As Figure 40 and Figure 41As shown, when the fluid machine operates, 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 moves in a circle 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 eccentricity of the corresponding first eccentric part 11 of 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 first slider 40 to move in a circle, 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 moves in a circle 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 corresponding second eccentric part 11 of 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 move in a circle, 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.

[0106] The fluid machine operating as above constitutes a cross slider mechanism, and the operating method adopts the principle of the cross slider mechanism, wherein the two eccentric parts 11 of the crankshaft 10 are respectively the first connecting rod L1 and the second connecting rod L2, the two limiting channels 31 of the cross groove structure 30 are respectively 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 (see Figure 40 ).

[0107] As shown in Figure 40 , the first connecting rod L1 and the second connecting rod L2 have a first included angle A, and the third connecting rod L3 and the fourth connecting rod L4 have a second included angle B, wherein the first included angle A is twice the second included angle B.

[0108] As shown in Figure 41 , the line between the axis O0 of the crankshaft 10 and the axis O1 of the cross groove structure 30 is the line O0 O1, the first connecting rod L1 and the line O0 O1 have a third included angle C, the corresponding third connecting rod L3 and the line O0 O1 have a fourth included angle D, wherein the third included angle C is twice the fourth included angle D; the second connecting rod L2 and the line O0 O1 have a fifth included angle E, and the corresponding fourth connecting rod L4 and the line O0 O1 have a sixth included angle F, wherein the fifth included angle E is twice the sixth included angle F; the sum of the third included angle C and the fifth included angle E is the first included angle A, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.

[0109] 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.

[0110] 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, 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, thereby driving the cross-groove structure 30 to rotate through the slider 40, and further driving the slider 40 at the dead point position to continue rotating 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, thereby ensuring the working reliability of the heat exchange equipment.

[0111] It should be noted that, in the present application, the maximum force arm of the driving torque of the eccentric part 11 is 2e.

[0112] 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.

[0113] It should be noted that, in the present application, in the process of rotating the crankshaft 10, the crankshaft 10 rotates 2 circles, and completes 4 times of suction and exhaust processes.

[0114] As Figures 1 to 39As 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 by 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.

[0115] Specifically, as shown in Figure 6 , the eccentricity of the two eccentric parts 11 is equal to e, as shown in 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), and the flange 50 comprises an upper flange 52 and a lower flange 53, as shown in Figure 8 , 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.

[0116] Optionally, the first assembly gap between the crankshaft 10 and the flange 50 is 0.005mm-0.05mm.

[0117] Preferably, the first assembly gap is 0.01-0.03mm.

[0118] 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.

[0119] 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.

[0120] As shown in Figures 2 to 7 , Figure 10 , Figure 11 , 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.

[0121] 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.

[0122] Optionally, the first segment and the second segment are detachably connected. In this way, the assembly and disassembly of the crankshaft 10 are facilitated.

[0123] As shown in Figures 2 to 7 , Figure 10 , Figure 11 , 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.

[0124] 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.

[0125] As shown in Figures 3 to 5 , 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.

[0126] 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.

[0127] Preferably, the first included angle A is 160 degrees, and the second included angle B is 80 degrees.

[0128] Preferably, the first included angle A is 165 degrees, and the second included angle B is 82.5 degrees.

[0129] Preferably, the first included angle A is 170 degrees, and the second included angle B is 85 degrees.

[0130] Preferably, the first included angle A is 175 degrees, and the second included angle B is 87.5 degrees.

[0131] Preferably, the first included angle A is 180 degrees, and the second included angle B is 90 degrees.

[0132] Preferably, the first included angle A is 185 degrees, and the second included angle B is 92.5 degrees.

[0133] Preferably, the first included angle A is 190 degrees, and the second included angle B is 95 degrees.

[0134] Preferably, the first included angle A is 195 degrees, and the second included angle B is 97.5 degrees.

[0135] 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 sliding block 40, thereby ensuring the movement reliability of the sliding block 40.

[0136] As shown in Figures 2 to 7 , Figure 10 , Figure 11 The eccentric portion 11 is cylindrical.

[0137] 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.

[0138] Optionally, the proximal end of the eccentric portion 11 protrudes from the outer circle of the shaft body portion 12 of the crankshaft 10.

[0139] 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.

[0140] It should be noted that in an embodiment of the present application not shown in the figure, the sliding block 40 comprises a plurality of sub-structures, which are spliced to form a through hole 41.

[0141] As shown in Figures 2 to 7 , Figure 10 , Figure 11 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 sliding blocks 40, it is ensured that the interval distance between the two eccentric portions 11 can provide assembly space for the cylinder sleeve 20, thereby ensuring assembly convenience.

[0142] As shown in Figure 3 , the cross-slot 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.

[0143] 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.

[0144] As shown in Figure 9As shown, the projection of the sliding block 40 in the axial direction of the through hole 41 has two straight line segments and an arc 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 sliding block 40, the sliding block 40 has second sliding surfaces matched with the first sliding surfaces, the sliding block 40 has a pressing surface 42 towards the end portion of the limiting channel 31, the pressing surface 42 serves as the head of the sliding block 40, the two second sliding surfaces are connected through the pressing surface 42, and the pressing surface 42 faces the variable volume cavity 311. In this way, the projection of the second sliding surface of the sliding block 40 in the axial direction of the through hole 41 is a straight line segment, and the projection of the pressing surface 42 of the sliding block 40 in the axial direction of the through hole 41 is an arc segment.

[0145] Specifically, the pressing 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 portion 11. Figure 9 In the embodiment, the center of the through hole 41 of the sliding block 40 is O 滑块 , the distance between the center of the arc surface and the center of the through hole 41 is e, i.e., the eccentricity of the eccentric portion 11, Figure 9 The X dotted line in the embodiment represents a circle on which the centers of the two arc surfaces are located.

[0146] Optionally, the radius of curvature of the arc surface is equal to the radius of the inner circle of the cylinder sleeve 20.

[0147] Optionally, the radius of curvature of the arc surface has a difference with the radius of the inner circle of the cylinder sleeve 20, and the difference is in the range of -0.05mm-0.025mm.

[0148] Preferably, the difference is in the range of -0.02-0.02mm.

[0149] It should be noted that in the present application, the projection area S 滑块 of the pressing surface 42 in the sliding direction of the sliding block 40 satisfies the following relationship with the area S 排 of the compression exhaust port 22 of the cylinder sleeve 20: S 滑块 / S 排 is in the range of 8-25.

[0150] Preferably, S 滑块 / S 排 is in the range of 12-18.

[0151] It should be noted that the fluid machine shown in the embodiment is a compressor, such as Figure 1As shown, the fluid machine comprises 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, wherein the distributor component 80 is arranged outside the housing assembly 81, the upper cover assembly 84 is assembled at the upper end of the housing assembly 81, the lower cover assembly 85 is assembled at 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, wherein the motor assembly 82 is located above the pump body assembly 83, or the motor assembly 82 is located below the pump body assembly 83. The pump body assembly 83 of the fluid machine comprises the crankshaft 10, the cylinder sleeve 20, the cross groove structure 30, the sliding block 40, the upper flange 52 and the lower flange 53 as described above.

[0152] Optionally, the above components are connected by welding, shrinkage or cold pressing.

[0153] The assembly process of the entire pump body assembly 83 is as follows: the lower flange 53 is fixed on the cylinder sleeve 20, the two sliding blocks 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 sliding blocks 40, and then the assembled crankshaft 10, cross groove structure 30 and two sliding blocks 40 are arranged in the cylinder sleeve 20, one end of the crankshaft 10 is installed on the lower flange 53, and the other end of the crankshaft 10 passes through the upper flange 52, which can be specifically referred to Figure 2 and Figure 3 .

[0154] It should be noted that, in the present embodiment, the closed space surrounded by the sliding block 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 2 turns, and a single variable volume chamber 311 completes one suction and exhaust process. For the fluid machine, the crankshaft 10 rotates 2 turns, and a total of four suction and exhaust processes are completed.

[0155] Further, the closed space surrounded by the extrusion surface 42 of the head of the sliding block 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, part of the surface of the upper flange 52 (or part of the surface of the lower flange 53) facing the cylinder sleeve 20 is the variable volume chamber 311.

[0156] The operation of the fluid machine will be described in detail as follows:

[0157] As Figure 1As 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.

[0158] To address the problem of insufficient air intake in fluid machinery, this invention supplements the aforementioned fluid machinery with the following details:

[0159] Example 1

[0160] like Figures 10 to 18 , Figure 46 As shown, the cylinder liner 20 of the fluid machinery has at least one radial intake hole 21, which is used to communicate with the variable volume chamber 311. The ratio S / V of the cross-sectional area S of the hole of a single radial intake hole 21 to the displacement V of the fluid machinery is in the range of 0.006 to 0.01.

[0161] By reasonably optimizing the ratio S / V of the cross-sectional area S of the radial intake hole 21 of the cylinder liner 20 to the displacement V of the fluid machinery within the range of 0.006 to 0.01, intake loss due to insufficient intake of the fluid machinery is avoided, thereby ensuring that the volumetric efficiency of the fluid machinery can reach its optimal value within this range.

[0162] like Figures 10 to 18 As shown, the inner wall of the cylinder liner 20 has an intake chamber 23, and the radial intake hole 21 communicates with the variable volume chamber 311 through the intake chamber 23. This ensures that the intake chamber 23 can store a large amount of gas, so that the variable volume chamber 311 can be fully saturated with gas, thereby enabling the fluid machinery to draw in sufficient gas. When the intake is insufficient, the stored gas can be supplied to the variable volume chamber 311 in a timely manner to ensure the compression efficiency of the fluid machinery.

[0163] Optionally, the intake chamber 23 is a cavity formed by radially hollowing out the inner wall surface of the cylinder liner 20. There can be one intake chamber 23 or two chambers, one above the other.

[0164] Specifically, the intake chamber 23 extends circumferentially around the inner wall of the cylinder liner 20 by a first predetermined distance to form an arc-shaped intake chamber 23. This ensures that the volume of the intake chamber 23 is large enough to store a large amount of gas.

[0165] like Figures 10 to 18As shown in the drawings, the suction cavities 23 are two, and the two suction cavities 23 are arranged along the axial direction of the cylinder sleeve 20, and the cylinder sleeve 20 further has a suction communication cavity 24, and the two suction cavities 23 are in communication with the suction communication cavity 24, and when the cylinder sleeve 20 has one radial suction hole 21, the radial suction hole 21 is in communication with the two suction cavities 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.

[0166] As shown in the drawings, Figures 10 to 18 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 ensures the machining convenience of the suction communication cavity 24.

[0167] As shown in the drawings, Figures 10 to 18 the radial suction hole 21 is symmetrical about the center line between the two end surfaces of the axial direction of the cylinder sleeve 20; the two suction cavities 23 are symmetrical about the center line between the two end surfaces of the axial direction of the cylinder sleeve 20; the suction communication cavity 24 includes two sub-suction communication cavities in communication, and the two sub-suction communication cavities are symmetrical about the center line between the two end surfaces of the axial direction of the cylinder sleeve 20. In this way, it ensures that the fluid machine is fully sucked, is beneficial to improve the performance and refrigerating capacity of the fluid machine, solves the problem of mutual interference between various parts in the design due to the small volume of the fluid machine, ensures that the design of the fluid machine is relatively easy, and ensures that the fluid machine can run smoothly and quietly.

[0168] Embodiment two

[0169] It should be noted that when the displacement of the upper and lower parts of the axial direction of the cylinder sleeve 20 of the fluid machine is not equal, the asymmetric suction mode of the cylinder sleeve 20 can be used, which is as follows:

[0170] As shown in the drawings, Figures 19 to 26 the radial suction hole 21 is asymmetrical about the center line between the two end surfaces of the axial direction of the cylinder sleeve 20; the two suction cavities 23 are asymmetrical about the center line between the two end surfaces of the axial direction of the cylinder sleeve 20; the suction communication cavity 24 includes two sub-suction communication cavities in communication, and the two sub-suction communication cavities are asymmetrical about the center line between the two end surfaces of the axial direction of the cylinder sleeve 20. In this way, the vibration and noise generated during the operation of the fluid machine are solved through the asymmetric design.

[0171] As shown in the drawings, Figure 22As shown, taking the centerline between the two end faces of the cylinder liner 20 along the axial direction as a reference, the diameter of the cavity cross-section of the sub-intake connecting cavity on the side closer to the radial intake port 21 is d1, and the diameter of the cavity cross-section of the sub-intake connecting cavity on the side farther from the radial intake port 21 is d2, where d1 < d2; the height of the intake cavity 23 on the side closer to the radial intake port 21 along the axial direction of the cylinder liner 20 is h1, and the height of the intake cavity 23 on the side farther from the radial intake port 21 along the axial direction of the cylinder liner 20 is h2, where h1 < h2. This ensures that the asymmetrical intake method of the cylinder liner 20 can solve the problem of unequal displacement between the upper and lower parts of the cylinder liner 20 along the axial direction.

[0172] Example 3

[0173] like Figures 27 to 33 As shown, there are two intake chambers 23, which are spaced apart along the axial direction of the cylinder liner 20. There are also two radial intake holes 21, each corresponding to one of the two intake chambers 23, and each radial intake hole 21 is connected to a corresponding variable volume chamber 311 through one of the two intake chambers 23. This ensures that the upper and lower parts of the cylinder liner 20 can form independent intake modes, ensuring that the two intake processes do not interfere with each other, and avoiding the phenomenon of reduced intake efficiency due to mutual interference between the upper and lower parts of the cylinder liner 20 during intake.

[0174] It should be noted that in this embodiment, there are two radial suction holes 21, wherein the ratio S / V of the cross-sectional area S of each radial suction hole 21 to the displacement V of the fluid machinery is in the range of 0.006 to 0.01.

[0175] The following describes the exhaust method of the fluid machinery of this application using the intake method of Embodiment 1. The exhaust method described below is applicable to the fluid machinery with the intake method described in Embodiments 2 and 3 above.

[0176] In the first exhaust embodiment, the upper flange 52 and the lower flange 53 are vented separately, as detailed below:

[0177] It should be noted that, in an embodiment not shown in this application, the fluid machinery further includes two flanges 50, which are respectively disposed at both axial ends of the cylinder liner 20. Each flange 50 has an exhaust channel 51 on its end face, and the two exhaust channels 51 are respectively connected to the variable volume chamber 311 on the corresponding side. In this way, the exhaust from the upper and lower flanges 50 replaces the existing cylinder liner-side exhaust. Since the side wall of the cylinder liner 20 is curved, the exhaust channels 51 are avoided from being located on the curved cylinder liner 20, and instead are located on the planes of the upper flange 52 and the lower flange 53, respectively, reducing the manufacturing difficulty of the exhaust channels 51.

[0178] Specifically, the end of the radial suction hole 21 is a compressed intake port, and the initial end of the exhaust passage 51 is a compressed exhaust port. When any one of the sliders 40 is in the intake position, the compressed intake port is in communication with the variable volume chamber 311 on the corresponding side. When any one of the sliders 40 is in the exhaust position, the variable volume chamber 311 on the corresponding side is in communication with the compressed exhaust port. In this way, when high-pressure gas enters the variable volume chamber 311 through the compressed intake port, the high-pressure gas drives the cross groove structure 30 to rotate, the cross groove structure 30 rotates to drive the slider 40 to rotate, and at the same time, the slider 40 linearly slides relative to the cross groove structure 30, thereby driving the slider 40 to rotate, i.e., driving the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can output work.

[0179] Other use occasions: the fluid machine can be used as an expander by exchanging the positions of the compressed intake port and the compressed exhaust port. That is, the compressed exhaust port is used as the suction port of the expander, high-pressure gas is introduced, other driving mechanisms rotate, and the gas is discharged through the compressed intake port (the exhaust port of the expander) after expansion.

[0180] Specifically, the end of the radial suction hole 21 is a compressed intake port, and the initial end of the exhaust passage 51 is a compressed exhaust port. When any one of the sliders 40 is in the intake position, the compressed intake port is in communication with the variable volume chamber 311 on the corresponding side. When any one of the sliders 40 is in the exhaust position, the variable volume chamber 311 on the corresponding side is in communication with the compressed exhaust port. In this way, when high-pressure gas enters the variable volume chamber 311 through the compressed intake port, the high-pressure gas drives the cross groove structure 30 to rotate, the cross groove structure 30 rotates to drive the slider 40 to rotate, and at the same time, the slider 40 linearly slides relative to the cross groove structure 30, thereby driving the slider 40 to rotate, i.e., driving the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can output work.

[0181] Exhaust embodiment two, cylinder liner side exhaust, specifically as follows:

[0182] As shown in Figures 34 to 36 The outer wall of the cylinder liner 20 is provided with an exhaust cavity 25, and the cylinder liner 20 further has an exhaust port 22 which is communicated to the exhaust cavity 25 from the inner wall of the cylinder liner 20. The fluid machine further comprises an exhaust valve assembly 60 which is arranged in the exhaust cavity 25 and corresponds to the exhaust port 22. In this way, the exhaust cavity 25 is used to accommodate the exhaust valve assembly 60, effectively reducing the occupied space of the exhaust valve assembly 60, reasonably arranging the components, and improving the space utilization of the cylinder liner 20.

[0183] As shown in Figures 34 to 36As shown, there are two exhaust ports 22, which are spaced apart along the axial direction of the cylinder liner 20. There are two sets of exhaust valve assemblies 60, which are respectively set for the two exhaust ports 22. In this way, since the two compression exhaust ports 22 are respectively equipped with two sets of exhaust valve assemblies 60, the large amount of gas leakage in the variable volume chamber 311 is effectively avoided, thus ensuring the compression efficiency of the variable volume chamber 311.

[0184] Furthermore, the exhaust valve assembly 60 is connected to the cylinder liner 20 via fasteners. The exhaust valve assembly 60 includes an exhaust valve plate and a valve plate baffle. The exhaust valve plate is disposed within the exhaust chamber 25 and blocks the corresponding compressed exhaust port 22. The valve plate baffle overlaps and is disposed on the exhaust valve plate. In this way, the valve plate baffle effectively prevents the exhaust valve plate from over-opening, thereby ensuring the exhaust performance of the cylinder liner 20.

[0185] Optionally, the fastener is a screw.

[0186] In one embodiment of this application (not shown), there is one exhaust chamber 25. At least one axial end face of the cylinder liner 20 is also provided with a connecting hole 26, which communicates with the exhaust chamber 25. The fluid machinery also includes two flanges 50, which are respectively disposed at both axial ends of the cylinder liner 20. The flange 50 opposite to the connecting hole 26 has an exhaust passage 51, which communicates with the connecting hole 26. This ensures the reliability of the exhaust from the cylinder liner 20.

[0187] like Figures 34 to 36 As shown, there are two exhaust ports 22, which are spaced apart along the axial direction of the cylinder liner 20. There are two exhaust chambers 25, which are arranged one-to-one with the two exhaust ports 22. There are two sets of exhaust valve assemblies 60, which are respectively arranged corresponding to the two exhaust ports 22.

[0188] like Figures 34 to 36 As shown, the two exhaust chambers 25 are connected by an exhaust port 28. At least one axial end face of the cylinder liner 20 is also provided with a connecting hole 26, which communicates with the exhaust chambers 25. The fluid machinery also includes two flanges 50, which are respectively located at both axial ends of the cylinder liner 20. The flange 50 opposite the connecting hole 26 has an exhaust passage 51, which communicates with the connecting hole 26. Thus, exhaust from the cylinder liner 20 side is then transferred to the exhaust passage 51 of the upper flange 52 for further exhaust.

[0189] In another embodiment of the application not shown in the drawings, the two exhaust chambers 25 are not communicated, and the two axial end faces of the cylinder sleeve 20 are each provided with a communication hole 26, the two communication holes 26 are respectively communicated with the two exhaust chambers 25, and the fluid machine further comprises two flanges 50, the two flanges 50 are respectively arranged at the axial two ends of the cylinder sleeve 20, and the flanges 50 opposite to the communication holes 26 are each provided with an exhaust passage 51, and the communication hole 26 is communicated with the exhaust passage 51. In this way, the upper and lower parts of the cylinder sleeve 20 are respectively subjected to side exhaust, and are then respectively converted into upper exhaust of the upper flange 52 and lower exhaust of the lower flange 53.

[0190] In the third exhaust embodiment, the cylinder sleeve is subjected to side exhaust and the flange is subjected to end face exhaust, and the specific implementation is as follows:

[0191] As shown in Figures 37 to 39 , the exhaust port 22 is one, and the exhaust port 22 is communicated with the corresponding variable volume chamber 311, and at least one axial end face of the cylinder sleeve 20 is further provided with a communication hole 26, and the communication hole 26 is communicated with the exhaust chamber 25; the fluid machine further comprises two flanges 50, the two flanges 50 are respectively arranged at the axial two ends of the cylinder sleeve 20, and the flange 50 opposite to the communication hole 26 in the two flanges 50 is provided with a first exhaust passage 511, and the communication hole 26 is communicated with the first exhaust passage 511; the flange 50 away from the exhaust port 22 of the two flanges 50 has a second exhaust passage 512, and the second exhaust passage 512 is communicated with the corresponding variable volume chamber 311. In this way, the side exhaust of the cylinder sleeve 20 is realized, and the end exhaust of the flange 50 is combined.

[0192] As shown in Figures 37 to 39 , the exhaust chamber 25 penetrates to the outer wall surface of the cylinder sleeve 20, and the fluid machine further comprises an exhaust cover plate 70, the exhaust cover plate 70 is connected with the cylinder sleeve 20 and seals the exhaust chamber 25. In this way, the exhaust cover plate 70 plays a role of separating the variable volume chamber 311 from the external space of the pump body assembly 83.

[0193] Specifically, the end of the radial suction hole 21 is a compression intake port, and the exhaust port 22 on the cylinder sleeve 20 is a compression exhaust port, when any one of the sliding blocks 40 is in the intake position, the compression intake port is communicated with the corresponding variable volume chamber 311; when any one of the sliding blocks 40 is in the exhaust position, the corresponding variable volume chamber 311 is communicated with the compression exhaust port. In this way, when the high-pressure gas enters the variable volume chamber 311 through the compression intake port, the high-pressure gas drives the cross groove structure 30 to rotate, the cross groove structure 30 rotates to drive the sliding block 40 to rotate, and at the same time, the sliding block 40 is linearly slid relative to the cross groove structure 30, and then the sliding block 40 drives the eccentric part 11 to rotate, that is, drives the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can output work.

[0194] Other use occasions: the fluid machine exchanges the positions of the suction and discharge ports, and can be used as an expander. That is, the compression discharge port of the fluid machine is used as the suction port of the expander, high-pressure gas is introduced, the other driving mechanism rotates, and the gas is discharged after expansion through the compression intake port (expander discharge port).

[0195] Specifically, the end of the radial suction hole 21 is the expansion discharge port, the exhaust port 22 on the cylinder sleeve 20 is the expansion intake port, when any one sliding block 40 is in the intake position, the expansion discharge port is communicated with the variable volume chamber 311 on the corresponding side; when any one sliding block 40 is in the exhaust position, the variable volume chamber 311 on the corresponding side is communicated with the expansion intake port. In this way, after the high-pressure gas enters the variable volume chamber 311 through the expansion intake port, the high-pressure gas drives the cross groove structure 30 to rotate, the cross groove structure 30 rotates to drive the sliding block 40 to rotate, and at the same time, the sliding block 40 is linearly slid relative to the cross groove structure 30, thereby driving the sliding block 40 to rotate, that is, driving the crankshaft 10 to rotate. By connecting the crankshaft 10 with other power-consuming equipment, the crankshaft 10 can output work.

[0196] Optionally, the inner wall surface of the cylinder sleeve 20 has an expansion discharge cavity, and the expansion discharge cavity is communicated with the expansion discharge port.

[0197] Further, the expansion discharge cavity extends by a first preset distance along the circumference of the inner wall surface of the cylinder sleeve 20 to form an arc-shaped expansion discharge cavity, and the expansion discharge cavity extends from the expansion discharge port to the side where the expansion intake port is located, and the extension direction of the expansion discharge cavity is the same as the rotation direction of the cross groove structure 30.

[0198] Further, the expansion discharge cavity is two, and the two expansion discharge cavities are arranged in the axial direction of the cylinder sleeve 20, the cylinder sleeve 20 further has an expansion discharge communication cavity, the two expansion discharge cavities are both communicated with the expansion discharge communication cavity, and the expansion discharge port is communicated with the expansion discharge cavity through the expansion discharge communication cavity.

[0199] Further, the expansion discharge communication cavity extends by a second preset distance along the axial direction of the cylinder sleeve 20, and at least one end of the expansion discharge communication cavity penetrates the axial end surface of the cylinder sleeve 20.

[0200] It is to 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 as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprise" and / or "include" when used in this specification, specify the presence of features, steps, operations, devices, components and / or combinations thereof.

[0201] The foregoing is a summary and thus contains only the most basic embodiment of the application. The application can be practiced with modification and alteration and can take many different forms. Specific embodiments of the application have been chosen for purposes of illustration and example, but are understood not to limit the scope of the application, except insofar as they appear in the appended claims. The foregoing summary as well as the following detailed description are not intended to restrict the scope of the present application, but are intended to embrace all changes and modifications that can come within the scope and spirit of the present application. All statements of a certain scope often apply to structural and / or method aspects of the present application. Thus, if there is a structural aspect that does not come within the scope of certain claim, then changes in that structural aspect can not change the scope of that claim, but need to addressed in changing described processes. In cases where the present application can not be amended to permit the claim, it is intended that each claim will cover the alternative having the capability to be amended. The elements of the embodiments shown in the figures are not necessarily to scale as has been described above, exemplified, and explained. Therefore, the dimensions of the various elements in the drawings can not be to scale and can have been arbitrarily increased or reduced in order to make the drawings and the descriptions herein easier to understand. It should be noted that all references to "a" or "an" can mean one or more than one unless the context clearly dictates otherwise. Any embodiment described herein as "comprising" the described elements can also "consist essentially of or "consist of the described elements.

[0202] For purposes of the US, the phrase "at least one of the preceding clauses" functions the same as "at least one of the preceding clauses to the extent that a jurisdiction recognizes it as having the same meaning." In the description above and in the claims, phrases such as "at least one of" or "one or more of" can occur followed by a conjunctive list of elements such as "a, b, c, and d". Any such phrases present in the claims are understood to perform the function of "at least one of a group consisting of a, b and d," i.e., either a, b, c or d, but not both. For example, the phrase "at least one of a and b" is understood to mean "a or b or a and b." Similar phrases, such as "one or more of," are to be interpreted in the same manner.

[0203] It is to be understood that the terminology used herein is for the purpose of describing the particular embodiments only and is not intended to be limiting, since the scope of the application will be 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. It will be appreciated that, where necessary, the terms used herein have been defined with either no hyphen or with a hyphen to indicate that the term is intended to encompass both the singular and plural forms of the term. 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.

[0204] It is to be understood that the terminology used herein is for the purpose of describing the particular embodiments only and is not intended to be limiting, since the scope of the application will be 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. It will be appreciated that, where necessary, the terms used herein have been defined with either no hyphen or with a hyphen to indicate that the term is intended to encompass both the singular and plural forms of the term. 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.

[0205] The above merely provides the preferred embodiments of the present application, and is not used to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modifications, equivalent replacements, improvements, etc. made within the principles and technical scope of the present application shall fall into the scope of the present application.

Claims

1. A fluid machine characterized by, The fluid machine comprises: a crankshaft (10) provided with two eccentric portions (11) along the axial direction thereof; a cylinder sleeve (20) eccentrically arranged with the crankshaft (10) and fixed in eccentric distance; a cross-groove structure (30) rotatably arranged in the cylinder sleeve (20), the cross-groove structure (30) being provided with two limiting channels (31) arranged in sequence 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); sliding blocks (40) provided with through holes (41), the sliding blocks (40) being two, the two eccentric portions (11) corresponding to extend into the through holes (41) of the two sliding blocks (40), the two sliding blocks (40) corresponding to be slidingly arranged in the two limiting channels (31) and forming a variable volume cavity (311), the variable volume cavity (311) being located in the sliding direction of the sliding blocks (40), the crankshaft (10) rotating to drive the sliding blocks (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 sliding blocks (40) rotate in the cylinder sleeve (20); wherein the cylinder sleeve (20) is provided with at least one radial air inlet hole (21) for communicating with the variable volume cavity (311), the ratio S / V of the cross-sectional area S of the hole section of the single radial air inlet hole (21) to the displacement V of the fluid machine being in the range of 0.006-0.

01.

2. The fluid machine of claim 1, wherein, The inner wall surface of the cylinder sleeve (20) is provided with an air inlet cavity (23), the radial air inlet hole (21) communicating with the variable volume cavity (311) through the air inlet cavity (23).

3. The fluid machine of claim 2, wherein, The air inlet cavity (23) extends a first preset distance around the circumference of the inner wall surface of the cylinder sleeve (20) to form an arc-shaped air inlet cavity (23).

4. The fluid machine of claim 2, wherein, The air inlet cavity (23) is two, the two air inlet cavities (23) being arranged in interval along the axial direction of the cylinder sleeve (20), the cylinder sleeve (20) being further provided with an air inlet communication cavity (24), the two air inlet cavities (23) both communicating with the air inlet communication cavity (24), when the cylinder sleeve (20) is provided with one radial air inlet hole (21), the radial air inlet hole (21) communicating with the two air inlet cavities (23) through the air inlet communication cavity (24).

5. The fluid machine of claim 4, wherein, The air inlet communication cavity (24) extends a second preset distance along the axial direction of the cylinder sleeve (20), at least one end of the air inlet communication cavity (24) penetrating through the axial end surface of the cylinder sleeve (20).

6. The fluid machine according to claim 4, wherein the radial air inlet hole (21) is symmetric about the center line between the two end surfaces of the axial direction of the cylinder sleeve (20); the two air inlet cavities (23) are symmetric about the center line between the two end surfaces of the axial direction of the cylinder sleeve (20); The suction communication cavity (24) comprises two sub-suction communication cavities in communication, and the two sub-suction communication cavities are symmetric about the center line between the two axial end faces of the cylinder sleeve (20).

7. The fluid machine according to claim 4, wherein, the radial suction hole (21) is asymmetric about the center line between the two axial end faces of the cylinder sleeve (20); the two suction cavities (23) are asymmetric about the center line between the two axial end faces of the cylinder sleeve (20); the suction communication cavity (24) comprises two sub-suction communication cavities in communication, and the two sub-suction communication cavities are asymmetric about the center line between the two axial end faces of the cylinder sleeve (20).

8. The fluid machine of claim 7, wherein, with the center line between the two axial end faces of the cylinder sleeve (20) as a reference, the diameter of the cavity section of the sub-suction communication cavity on the side away from the axis of the radial suction hole (21) is d1, and the diameter of the cavity section of the sub-suction communication cavity on the side close to the axis of the radial suction hole (21) is d2, wherein d1 < d2; the height of the suction cavity (23) on the side away from the axis of the radial suction hole (21) in the axial direction of the cylinder sleeve (20) is h1, and the height of the suction cavity (23) on the side close to the axis of the radial suction hole (21) in the axial direction of the cylinder sleeve (20) is h2, wherein h1 < h2.

9. The fluid machine of claim 2, wherein, The suction cavities (23) are two, the two suction cavities (23) are arranged in the axial direction of the cylinder sleeve (20) at intervals, the radial suction holes (21) are two, the two radial suction holes (21) correspond to the two suction cavities (23) one-to-one, and the two radial suction holes (21) respectively communicate with the corresponding variable volume cavities (311) through the two suction cavities (23).

10. The fluid machine of claim 1, wherein, The fluid machine further comprises two flanges (50), the two flanges (50) are respectively arranged at the two axial ends of the cylinder sleeve (20), and exhaust passages (51) are formed in the end faces of the two flanges (50), the two exhaust passages (51) respectively communicate with the variable volume cavities (311) on the corresponding sides.

11. The fluid machine of claim 10, wherein, The end of the radial suction hole (21) is a compressed air inlet, and the initial end of the exhaust passage (51) is a compressed air outlet, when any one of the sliders (40) is in the air inlet position, the compressed air inlet is in communication with the variable volume cavity (311) on the corresponding side; when any one of the sliders (40) is in the air outlet position, the variable volume cavity (311) on the corresponding side is in communication with the compressed air outlet.

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

13. The fluid machine of claim 10, wherein, The end of the radial suction hole (21) is an expanded air outlet, and the initial end of the exhaust passage (51) is an expanded air inlet, when any one of the sliders (40) is in the air inlet position, the expanded air outlet is in communication with the variable volume cavity (311) on the corresponding side; when any one of the sliders (40) is in the air outlet position, the variable volume cavity (311) on the corresponding side is in communication with the expanded air inlet.

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

15. The fluid machine of claim 1, wherein, The outer wall of the cylinder liner (20) is provided with an exhaust cavity (25), the cylinder liner (20) is further provided with an exhaust port (22), the exhaust port (22) is communicated to the exhaust cavity (25) by the inner wall of the cylinder liner (20), and the fluid machine further comprises an exhaust valve assembly (60), the exhaust valve assembly (60) is arranged in the exhaust cavity (25) and corresponds to the exhaust port (22).

16. The fluid machine of claim 15, wherein, The exhaust port (22) is two, the two exhaust ports (22) are arranged in the axial direction of the cylinder liner (20), and the exhaust valve assembly (60) is two groups, and the two groups of exhaust valve assemblies (60) are arranged correspondingly to the two exhaust ports (22).

17. The fluid machine of claim 16, wherein, The exhaust cavity (25) is one, at least one axial end surface of the cylinder liner (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 two flanges (50), the two flanges (50) are arranged at the axial two ends of the cylinder liner (20) respectively, and the flange (50) opposite to the communication hole (26) in the two flanges (50) is provided with an exhaust passage (51), and the communication hole (26) is communicated with the exhaust passage (51).

18. The fluid machine of claim 15, wherein, The exhaust port (22) is two, the two exhaust ports (22) are arranged in the axial direction of the cylinder liner (20), and the exhaust cavity (25) is two, the two exhaust cavities (25) are arranged one by one corresponding to the two exhaust ports (22), and the exhaust valve assembly (60) is two groups, and the two groups of exhaust valve assemblies (60) are arranged correspondingly to the two exhaust ports (22).

19. The fluid machine of claim 18, wherein, The two exhaust cavities (25) are communicated through an exhaust communication port (28), at least one axial end surface of the cylinder liner (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 two flanges (50), the two flanges (50) are arranged at the axial two ends of the cylinder liner (20) respectively, and the flange (50) opposite to the communication hole (26) in the two flanges (50) is provided with an exhaust passage (51), and the communication hole (26) is communicated with the exhaust passage (51).

20. The fluid machine of claim 18, wherein, The two exhaust cavities (25) are not communicated, the two axial end surfaces of the cylinder liner (20) are both provided with a communication hole (26), the two communication holes (26) are respectively communicated with the two exhaust cavities (25), and the fluid machine further comprises two flanges (50), the two flanges (50) are arranged at the axial two ends of the cylinder liner (20) respectively, and the flange (50) opposite to the communication hole (26) in the two flanges (50) is provided with an exhaust passage (51), and the communication hole (26) is communicated with the exhaust passage (51).

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

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

23. The fluid machine of any one of claims 15 to 22, wherein, The end of the radial suction hole (21) is a compression intake port, and the exhaust port (22) on the cylinder sleeve (20) is a compression exhaust port, When any one of the sliding blocks (40) is in the intake position, the compression intake port is in communication with the variable volume chamber (311) on the corresponding side; When any one of the sliding blocks (40) is in the exhaust position, the variable volume chamber (311) on the corresponding side is in communication with the compression exhaust port.

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

25. The fluid machine of any one of claims 15 to 22, wherein, The end of the radial suction hole (21) is an expansion exhaust port, and the exhaust port (22) on the cylinder sleeve (20) is an expansion intake port, When any one of the sliding blocks (40) is in the intake position, the expansion exhaust port is in communication with the variable volume chamber (311) on the corresponding side; When any one of the sliding blocks (40) is in the exhaust position, the variable volume chamber (311) on the corresponding side is in communication with the expansion intake port.

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

27. The fluid machine of claim 1, wherein, The two eccentric parts (11) have a phase difference of a first included angle A, the eccentric amounts of the two eccentric parts (11) are equal, and the extension directions of the two limit channels (31) have a phase difference of a second included angle B, wherein the first included angle A is twice the second included angle B.

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

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