CN117145770A - Fluid machine and heat exchange device - Google Patents
Fluid machine and heat exchange device Download PDFInfo
- Publication number
- CN117145770A CN117145770A CN202210565498.0A CN202210565498A CN117145770A CN 117145770 A CN117145770 A CN 117145770A CN 202210565498 A CN202210565498 A CN 202210565498A CN 117145770 A CN117145770 A CN 117145770A
- Authority
- CN
- China
- Prior art keywords
- eccentric
- crankshaft
- fluid machine
- groove structure
- cross groove
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 55
- 230000002093 peripheral effect Effects 0.000 claims abstract description 11
- 238000007789 sealing Methods 0.000 claims description 19
- 238000003825 pressing Methods 0.000 claims description 17
- 238000001125 extrusion Methods 0.000 claims description 6
- 238000007906 compression Methods 0.000 description 25
- 238000004891 communication Methods 0.000 description 22
- 230000006835 compression Effects 0.000 description 22
- 238000000034 method Methods 0.000 description 21
- 230000007246 mechanism Effects 0.000 description 19
- 230000008569 process Effects 0.000 description 16
- 208000028659 discharge Diseases 0.000 description 8
- 230000000694 effects Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 238000005461 lubrication Methods 0.000 description 4
- 230000000712 assembly Effects 0.000 description 3
- 238000000429 assembly Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000005457 optimization Methods 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 238000012795 verification Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
Abstract
The invention provides a fluid machine and heat exchange equipment, wherein the fluid machine comprises a crankshaft, a cylinder sleeve, a cross groove structure and a sliding block, and the crankshaft is axially provided with two eccentric parts; the crankshaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve, the cross groove structure and the cylinder sleeve are coaxially arranged, a first radial clearance C1 is formed between the outer peripheral surface of the cross groove structure and the inner wall surface of the cylinder sleeve, the range of the first radial clearance C1 is 0.01-0.08 mm, two limiting channels of the cross groove structure are sequentially arranged along the axial direction of the crankshaft, and the extending direction of the limiting channels is perpendicular to the axial direction of the crankshaft; 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 in a sliding mode and form a variable-volume cavity, and the variable-volume cavity is located in the sliding direction of the sliding blocks. The invention solves the problems of lower energy efficiency, higher noise and optimal comprehensive efficiency of the compressor in the prior art.
Description
Technical Field
The invention relates to the technical field of heat exchange systems, in particular to a fluid machine and heat exchange equipment.
Background
The fluid machinery in the prior art includes compressors, expanders, and the like. Taking a compressor as an example.
According to national energy-saving and environment-friendly policies and consumer requirements for air conditioning comfort, the air conditioning industry is always pursuing high efficiency and low noise. The compressor acts as the heart of the air conditioner, having a direct impact on the energy efficiency and noise level of the air conditioner. The rolling rotor type compressor is used as a main stream of household air conditioner compressors, has been developed for nearly one hundred years, is relatively mature, is limited by a structural principle, and has limited optimization space. Therefore, it is highly desirable to provide a compressor having the characteristics of high energy efficiency, low noise, and the like.
In addition, the larger the clearance between the friction pairs is, the smaller the power consumption of the friction pairs is, and the mechanical efficiency of the compressor is improved, in consideration of the fact that the clearance of each friction pair of the compressor has larger influence on energy efficiency; however, the leakage phenomenon occurs when the gap is too large, so that the volumetric efficiency of the compressor is reduced, and therefore, the gap at each part of the compressor needs to be reasonably designed to ensure that the comprehensive efficiency of the compressor can be optimized.
Disclosure of Invention
The invention mainly aims to provide a fluid machine and heat exchange equipment, which are used for solving the problems of low energy efficiency, high noise and optimal comprehensive efficiency of a compressor in the prior art.
In order to achieve the above object, according to one aspect of the present invention, there is provided a fluid machine including a crankshaft, a cylinder liner, a cross groove structure, and a slider, wherein the crankshaft is provided with two eccentric portions in an axial direction thereof; the crankshaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; the cross groove structure is rotatably arranged in the cylinder sleeve, the cross groove structure and the cylinder sleeve are coaxially arranged, a first radial clearance C1 is formed between the outer peripheral surface of the cross groove structure and the inner wall surface of the cylinder sleeve, the range of the first radial clearance C1 is 0.01-0.08 mm, the cross groove structure is provided with two limiting channels, the two limiting channels are sequentially arranged along the axial direction of the crankshaft, and the extending direction of the limiting channels is perpendicular to the axial direction of the crankshaft; the sliding block is provided with two through holes, 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 in a sliding mode 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 slide back and forth in the limiting channels and interact with the cross groove structure, so that the cross groove structure and the sliding block rotate in the cylinder sleeve.
Further, the first radial clearance C1 is in the range of 0.015 to 0.03mm.
Further, the cross groove structure is provided with a central hole, the two limiting channels are communicated through the central hole, and the aperture of the central hole is larger than the diameter of the shaft body part of the crankshaft.
Further, the aperture of the central hole is larger than the diameter of the eccentric part, a second radial clearance C2 is arranged between the wall surface of the central hole and the outer peripheral surface of the eccentric part, and the range of the second radial clearance C2 is 0.05-1 mm.
Further, the inner diameter D of the cylinder liner Cylinder sleeve Diameter d of outer circle of cross groove structure Groove(s) The following are satisfied: d (D) Cylinder sleeve ＝d Groove(s) +2c1; hole diameter D of center hole Limiting the limit Diameter d of eccentric portion Offset of deflection The following are satisfied: d (D) Limiting the limit ＝d Offset of deflection +2C2。
Further, the sliding block is provided with an extrusion surface facing the end part of the limiting channel, the extrusion surface is used as the head part of the sliding block, and the extrusion surface faces the variable-volume cavity; the extrusion surface is a cambered surface, a sealing distance M is arranged between the top end of the cambered surface and the hole wall surface of the central hole, and the sealing distance M periodically changes along with the sliding of the sliding block in the limiting channel.
Further, the sealing distance M has a minimum sealing distance M Minimum of Minimum seal distance M Minimum of The range of (2) is 1-6 mm.
Further, a minimum seal distance M Minimum of The range of (2) to (4) mm.
Further, the sealing distance M has a minimum sealing distance M Minimum of Outer circle diameter d of cross groove structure Groove(s) Hole diameter D of center hole Limiting the limit The eccentric amount e of the eccentric part satisfies: d, d Groove(s) ＝D Limiting the limit +8e+2M Minimum of 。
Further, the eccentric portion is cylindrical, and a proximal end of the eccentric portion protrudes from an outer circumference of the shaft body portion of the crankshaft.
Further, the protrusion amount T of the proximal end of the eccentric portion satisfies: t > 0.
Further, the protrusion amount T of the proximal end of the eccentric portion is in the range of 0.1 to 2mm.
Further, the protrusion T of the proximal end of the eccentric portion and the diameter d of the eccentric portion Offset of deflection Diameter d of shaft body part Shaft The eccentric amount e of the eccentric part satisfies: d, d Offset of deflection ＝d Shaft +2e+2T。
Further, a phase difference of a first included angle A is formed between the two eccentric parts, the eccentric amounts of the two eccentric parts are equal, and a phase difference of a second included angle B is formed between the extending directions of the two limiting channels, wherein the first included angle A is twice the second included angle B.
According to another aspect of the present invention, there is provided a heat exchange apparatus comprising a fluid machine, the fluid machine being the fluid machine described above.
By applying the technical scheme of the invention, based on the principle of optimizing the comprehensive efficiency of the fluid machine, the radial dimension relation of the pump body component of the fluid machine is defined, and scheme optimization is carried out for each design variable influencing the radial dimension, so that the mechanical efficiency and the volumetric efficiency of the fluid machine are ensured to be in a better range, and the comprehensive energy efficiency of the fluid machine is ensured to be optimal.
Further, in consideration of the fact that the first radial clearance C1 between the outer peripheral surface of the crossed groove structure and the inner wall surface of the cylinder sleeve is filled with lubricating oil in the running process of the fluid machine, the lubricating mode between the crossed groove structure and the cylinder sleeve is hydrodynamic lubrication, and under the hydrodynamic lubrication mode, the larger the clearance is, the larger the friction power consumption is, and the higher the mechanical efficiency of the fluid machine is; meanwhile, in the running process of the fluid machinery, the pressure difference exists between the air at the end parts of the sliding block at the two sides of the sliding direction, the air suction pressure is arranged on the side communicated with the air suction channel, the middle pressure or the exhaust pressure in the compression process is arranged at the other end, the air leaks from the high pressure side to the low pressure side through a first radial clearance C1 between the cross groove structure and the cylinder sleeve, the smaller the clearance at the low pressure side is, the better the tightness is, the smaller the leakage is, and the volumetric efficiency of the fluid machinery is higher.
In summary, the influence of the first radial clearance C1 on the mechanical efficiency and the volumetric efficiency is opposite, and theoretical analysis and experimental verification prove that the range of the first radial clearance C1 is reasonably optimized, so that the first radial clearance C1 is positioned in the range of 0.01-0.08 mm, and the comprehensive efficiency of the fluid machinery can be improved.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:
fig. 1 illustrates an internal structure of a compressor according to an alternative embodiment of the present application;
FIG. 2 shows a schematic structural view of a pump body assembly of the compressor of FIG. 1;
FIG. 3 shows an exploded view of the pump body assembly of FIG. 2;
FIG. 4 shows a schematic structural view of a cylinder liner of the pump body assembly of FIG. 3;
FIG. 5 shows a schematic structural view of the cross slot configuration of the pump body assembly of FIG. 3;
FIG. 6 shows a schematic structural view of the shaft body portion and the eccentric amounts of the two eccentric portions of the crankshaft of FIG. 3;
fig. 7 shows an enlarged schematic view of the structure at F in fig. 6;
FIG. 8 shows a schematic structural view of a seal distance M between the top end of the pressing surface of the head of the slider of the pump body assembly of FIG. 3 and the wall surface of the central bore of the cross-slot structure;
FIG. 9 shows a schematic structural view of a seal distance M between the top end of the pressing surface of the head of the slider of the pump body assembly of FIG. 3 and the wall surface of the central bore of the cross-slot structure;
FIG. 10 shows a schematic view of the cylinder liner and lower flange of the pump body assembly of FIG. 3 in an exploded condition;
FIG. 11 is a schematic view showing the structure of the eccentricity between the cylinder liner and the lower flange of FIG. 10;
FIG. 12 is a schematic cross-sectional structural view showing the amount of assembly eccentricity of the crankshaft and cylinder liner of FIG. 3;
FIG. 13 shows a schematic view of the slider of FIG. 3 in the axial direction of the through hole;
FIG. 14 is a schematic view showing a state structure of the compressor of FIG. 3 at the start of suction;
FIG. 15 is a schematic view showing a state structure of the compressor of FIG. 3 during suction;
FIG. 16 is a schematic view showing a state structure of the compressor of FIG. 3 at the end of suction;
FIG. 17 is a schematic view showing a state structure of the compressor of FIG. 3 when compressed gas is supplied;
FIG. 18 is a schematic view showing a state structure of the compressor of FIG. 3 in a discharge process;
FIG. 19 is a schematic view showing a state structure of the compressor of FIG. 3 at the end of discharge;
FIG. 20 illustrates a schematic mechanical diagram of the operation of a compressor in accordance with an alternative embodiment of the present invention;
FIG. 21 is a schematic diagram showing the principle of the mechanism of operation of the compressor of FIG. 20;
FIG. 22 is a schematic diagram showing the mechanism of operation of a prior art compressor;
FIG. 23 is a schematic diagram showing the mechanism of operation of the compressor modified in the prior art;
FIG. 24 is a schematic view of the mechanism of operation of the compressor of FIG. 23 showing the moment arm of the drive shaft driving the slider in rotation;
FIG. 25 is a schematic view showing the principle of the mechanism of operation of the compressor of FIG. 23, wherein the center of the limit slot structure coincides with the center of the eccentric portion;
FIG. 26 shows a graph of the effect of the first radial clearance C1 on the respective efficiencies of the compressor;
FIG. 27 shows a graph of the effect of the second radial clearance C2 on the mechanical efficiency of the compressor;
FIG. 28 is a graph showing the effect of minimum seal distance on various efficiencies of the compressor;
fig. 29 shows a graph of the effect of the minimum protrusion on the mechanical efficiency of the compressor.
Wherein the above figures include the following reference numerals:
10. a crankshaft; 11. a eccentric portion; 12. a shaft body portion;
20. cylinder sleeve; 21. a compression intake; 22. an exhaust port; 23. an air suction cavity; 24. an air suction communication cavity; 25. an exhaust chamber; 26. a communication hole;
30. a cross slot structure; 31. a limiting channel; 311. a variable volume chamber; 32. a central bore;
40. a slide block; 41. a through hole; 42. extruding the surface;
50. A flange; 52. an upper flange; 53. a lower flange;
60. an exhaust valve assembly;
70. an exhaust cover plate;
80. a knockout component; 81. a housing assembly; 82. a motor assembly; 83. a pump body assembly; 84. an upper cover assembly; 85. a lower cover assembly;
90. a fastener.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In the prior art, as shown in FIG. 22, a compressor operating mechanism principle is proposed based on a crosshead shoe mechanism, i.e., at point O 1 As cylinder center, point O 2 As the center of the driving shaft, point O 3 As the center of the slide block, the cylinder is eccentrically arranged with the driving shaft, wherein the center O of the slide block 3 At a diameter of O 1 O 2 Is moved circularly on a circle.
In the operating mechanism principle, the cylinder center O 1 And drive shaft center O 2 As two rotation centers of the movement mechanism, simultaneously, line segment O 1 O 2 Is the midpoint O of (1) 0 As the center O of the slide block 3 So that the slide is reciprocated relative to the cylinder and also to the drive shaft.
Due to line segment O 1 O 2 Is the midpoint O of (1) 0 As a virtual center, a problem of deterioration of high-frequency vibration characteristics of a compressor due to failure to provide a balance system, based on the principle of the above-described operation mechanism, as shown in fig. 23, a method of using O 0 As a movement mechanism of the drive shaft center, i.e. cylinder center O 1 And drive shaft center O 0 As two rotation centers of the motion mechanism, the driving shaft is provided with an eccentric part, the sliding block is coaxially arranged with the eccentric part, and the assembly eccentric amount of the driving shaft and the cylinder is equal to the eccentric amount of the eccentric part, so that the sliding block is provided with a center O 3 About the drive axis center O 0 Is used as the center of a circle and takes O as 1 O 0 Circular motion is performed for the radius.
The corresponding one set of running mechanism is proposed, including cylinder, spacing groove structure, slider and drive shaft, wherein, spacing groove structure rotationally sets up in the cylinder, and cylinder and spacing groove structure coaxial setting, i.e. cylinder center O 1 The sliding block is assembled coaxially with the eccentric part of the driving shaft, the sliding block performs circular motion around the shaft body part of the driving shaft, and the specific motion process is as follows: the driving shaft rotates to drive the sliding block to revolve around the center of the shaft body part of the driving shaft, the sliding block rotates relative to the eccentric part at the same time, and the sliding block reciprocates in the limiting groove of the limiting groove structure and pushes the limiting groove structure to rotate.
However, as shown in fig. 24, the length of the arm L of force for driving the rotation of the slider is l=2e×cos θ×cos θ, where e is the eccentric amount of the eccentric portion, and θ is O 1 O 0 Between the connecting line and the sliding direction of the sliding block in the limiting grooveAnd an included angle.
As shown in FIG. 25, when the cylinder is centered at O 1 When the center of the limit groove structure and the center of the eccentric portion are coincident, the resultant force of the driving shaft passes through the center of the limit groove structure, that is, the torque applied to the limit groove structure is zero, the limit groove structure cannot rotate, and the movement mechanism is at the dead point position and cannot drive the sliding block to rotate.
Based on this, the present application proposes a new mechanism principle of the cross groove structure 30 with two limiting channels 31 and two sliding blocks 40, and constructs a new compressor based on the principle, the compressor has the characteristics of high energy efficiency and low noise, and the following describes a compressor based on the cross groove structure 30 with two limiting channels 31 and two sliding blocks 40 specifically by taking the compressor as an example.
In order to solve the problems of low energy efficiency, high noise and optimal comprehensive efficiency of the compressor in the prior art, the invention provides a fluid machine and a heat exchange device, wherein the heat exchange device comprises the fluid machine, and the fluid machine is the fluid machine.
The fluid machinery comprises a crankshaft 10, a cylinder sleeve 20, a cross groove structure 30 and a sliding block 40, wherein the crankshaft 10 is axially provided with two eccentric parts 11, a phase difference of a first included angle A is formed between the two eccentric parts 11, and the eccentric amounts of the two eccentric parts 11 are equal; the crankshaft 10 and the cylinder sleeve 20 are eccentrically arranged, and the eccentric distance is fixed; the cross groove structure 30 is rotatably arranged in the cylinder sleeve 20, the cross groove structure 30 is provided with two limiting channels 31, the two limiting channels 31 are sequentially arranged along the axial direction of the crankshaft 10, the extending direction of the limiting channels 31 is perpendicular to the axial direction of the crankshaft 10, and a phase difference of a second included angle B is arranged between the extending directions of the two limiting channels 31, wherein the first included angle A is twice the second included angle B; the sliding blocks 40 are provided with through holes 41, the two eccentric parts 11 correspondingly extend into the two through holes 41 of the two sliding blocks 40, the two sliding blocks 40 are correspondingly arranged in the two limiting channels 31 in a sliding mode and form a variable-volume cavity 311, the variable-volume cavity 311 is positioned in the sliding direction of the sliding blocks 40, the crankshaft 10 rotates to drive the sliding blocks 40 to slide back and forth in the limiting channels 31 and interact with the cross groove structure 30, and the cross groove structure 30 and the sliding blocks 40 rotate in the cylinder sleeve 20.
By arranging the cross groove structure 30 in a structure form with two limiting channels 31 and correspondingly arranging two sliding blocks 40, two eccentric parts 11 of a crankshaft correspondingly extend into two through holes 41 of the two sliding blocks 40, simultaneously, the two sliding blocks 40 correspondingly slide in the two limiting channels 31 and form a variable volume cavity 311, as a first included angle A between the two eccentric parts 11 is twice as large as a second included angle B between extending directions of the two limiting channels 31, when one of the two sliding blocks 40 is at a dead point position, namely, the driving torque of the eccentric part 11 corresponding to the sliding block 40 at the dead point position is 0, the sliding block 40 at the dead point position cannot continuously rotate, and at the moment, the driving torque of the other eccentric part 11 of the two eccentric parts 11 drives the corresponding sliding block 40 to be the maximum value, so that the corresponding sliding block 40 can be normally driven to rotate by the sliding block 40, the cross groove structure 30 is driven to rotate by the cross groove structure 30, the sliding block 40 at the dead point position is driven to continuously rotate by the cross groove structure 30, the reliability of the mechanical movement of the fluid is ensured, the mechanical movement is avoided, and the reliability of the mechanical movement is ensured, and the working reliability is ensured.
In addition, the fluid machinery provided by the application can stably run, namely, the energy efficiency of the compressor is ensured to be higher, the noise is lower, and therefore, the working reliability of the heat exchange equipment is ensured.
In the present application, the first angle a and the second angle B are not zero.
As shown in fig. 20 and 21, when the fluid machine described above is operated, the crankshaft 10 is wound around the axial center O of the crankshaft 10 0 Autorotation; the cross groove structure 30 is formed around the axial center O of the crankshaft 10 0 Revolution, the axis O of the crankshaft 10 0 With the axis O of the cross slot structure 30 1 The eccentric arrangement is carried out with fixed eccentric distance; the first slide block 40 is arranged at the axis O of the crankshaft 10 0 The center O of the first slide 40 moves circularly 3 With the axis O of the crankshaft 10 0 The distance therebetween is equal to the curveThe first eccentric part 11 corresponding to the shaft 10 has an eccentric amount equal to the axis O of the crankshaft 10 0 With the axis O of the cross slot structure 30 1 The eccentric distance between the two sliding blocks, the crankshaft 10 rotates to drive the first sliding block 40 to do circular motion, and the first sliding block 40 interacts with the cross groove structure 30 and slides reciprocally in the limiting channel 31 of the cross groove structure 30; the second slide block 40 is arranged at the axis O of the crankshaft 10 0 A center O of the second slide 40 moves circularly for the center of the circle 4 With the axis O of the crankshaft 10 0 The distance between the two eccentric parts is equal to the eccentric amount of the second eccentric part 11 corresponding to the crankshaft 10, and the eccentric amount is equal to the axis O of the crankshaft 10 0 With the axis O of the cross slot structure 30 1 The eccentric distance between them, the crankshaft 10 rotates to drive the second slider 40 to do circular motion, and the second slider 40 interacts with the cross slot structure 30 and slides reciprocally in the limiting channel 31 of the cross slot structure 30.
The fluid machine operating as described above constitutes a slider-cross mechanism, which employs the slider-cross mechanism principle, wherein the two eccentric portions 11 of the crankshaft 10 are each provided as a first connecting rod L 1 And a second connecting rod L 2 The two limiting channels 31 of the cross slot structure 30 are respectively used as the third connecting rod L 3 And a fourth connecting rod L 4 And a first link L 1 And a second connecting rod L 2 Is equal (see fig. 20).
As shown in fig. 20, a first link L 1 And a second connecting rod L 2 A first included angle A and a third connecting rod L are arranged between 3 And a fourth connecting rod L 4 The first included angle A is twice as large as the second included angle B.
As shown in fig. 21, the axis O of the crankshaft 10 0 With the axis O of the cross slot structure 30 1 The connection line between the two is connection line O 0 O 1 First connecting rod L 1 And connecting line O 0 O 1 A third included angle C is formed between the two connecting rods, and a corresponding third connecting rod L 3 And connecting line O 0 O 1 A fourth included angle D is formed between the first and second inclined angles, wherein the third included angle C is twice the fourth included angle D; second connecting rod L 2 And connecting line O 0 O 1 With a gap therebetweenA fifth included angle E and a corresponding fourth connecting rod L 4 And connecting line O 0 O 1 A sixth included angle F is formed between the two surfaces, wherein the fifth included angle E is twice as large as the sixth included angle F; the sum of the third included angle C and the fifth included angle E is a first included angle A, and the sum of the fourth included angle D and the sixth included angle F is a second included angle B.
Further, the operation method further comprises the rotation angular velocity of the sliding block 40 relative to the eccentric part 11 and the rotation angular velocity of the sliding block 40 around the axis O of the crankshaft 10 0 The revolution angular velocity of (2) is the same; the cross groove structure 30 is formed around the axial center O of the crankshaft 10 0 The revolution angular velocity of the slider 40 is the same as the rotation angular velocity of the eccentric portion 11.
Specifically, the axis O of the crankshaft 10 0 Equivalent to the first connecting rod L 1 And a second connecting rod L 2 The center of rotation O of the cross slot structure 30 1 Corresponds to the third connecting rod L 3 And a fourth connecting rod L 4 Is provided; the two eccentric portions 11 of the crankshaft 10 serve as first connecting rods L, respectively 1 And a second connecting rod L 2 The two limiting channels 31 of the cross slot structure 30 are respectively used as the third connecting rod L 3 And a fourth connecting rod L 4 And a first link L 1 And a second connecting rod L 2 So that the eccentric portion 11 of the crankshaft 10 drives the corresponding slide block 40 around the axis O of the crankshaft 10 while the crankshaft 10 rotates 0 Revolution is carried out, meanwhile, the sliding blocks 40 can rotate relative to the eccentric part 11, and the relative rotation speeds of the two sliding blocks are the same, because the first sliding block 40 and the second sliding block 40 respectively reciprocate in the two corresponding limiting channels 31 and drive the cross groove structure 30 to do circular motion, the two sliding blocks 40 always have the phase difference of a second included angle B in the motion direction due to the limit of the two limiting channels 31 of the cross groove structure 30, when one of the two sliding blocks 40 is at the dead point position, the eccentric part 11 for driving the other one of the two sliding blocks 40 has the maximum driving torque, the eccentric part 11 with the maximum driving torque can normally drive the corresponding sliding block 40 to rotate, thereby driving the cross groove structure 30 to rotate through the sliding block 40, and further driving the sliding block 40 at the dead point position to continue rotating through the cross groove structure 30, thereby realizing the stable operation of the fluid machinery and avoiding the motion mechanismAnd the dead point position improves the movement reliability of the fluid machinery, thereby ensuring the working reliability of the heat exchange equipment.
In the present application, the maximum arm of the driving torque of the eccentric portion 11 is 2e.
In this movement method, the running track of the slider 40 is a circle, and the circle is about the axis O of the crankshaft 10 0 With the line O as the center of a circle 0 O 1 Is a radius.
In the present application, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 times to complete 4 intake and exhaust processes.
As shown in fig. 1 to 19, the fluid machine further includes a flange 50, the flange 50 is disposed at an axial end portion of the cylinder liner 20, the crankshaft 10 is disposed concentrically with the flange 50, the cross groove structure 30 is disposed coaxially with the cylinder liner 20, an assembly eccentricity of the crankshaft 10 and the cross groove structure 30 is determined by a relative positional relationship between the flange 50 and the cylinder liner 20, wherein the flange 50 is fixed on the cylinder liner 20 by a fastener 90, a relative position of an axial center of the flange 50 and an axial center of an inner ring of the cylinder liner 20 is controlled by aligning the flange 50, and a relative position of the axial center of the flange 50 and the axial center of the inner ring of the cylinder liner 20 determines a relative position of the axial center of the crankshaft 10 and the axial center of the cross groove structure 30, and an eccentric amount of the eccentric portion 11 is equal to an assembly eccentricity of the crankshaft 10 and the cylinder liner 20 by an essence of aligning the flange 50.
Specifically, as shown in fig. 6, the eccentric amounts of the two eccentric portions 11 are equal to e, as shown in fig. 12, the fitting eccentric amount between the crankshaft 10 and the cylinder liner 20 is e (since the cross groove structure 30 is coaxially provided with the cylinder liner 20, the fitting eccentric amount between the crankshaft 10 and the cross groove structure 30, that is, the fitting eccentric amount between the crankshaft 10 and the cylinder liner 20), and the flange 50 includes an upper flange 52 and a lower flange 53, as shown in fig. 11, the distance between the inner ring axis of the cylinder liner 20 and the inner ring axis of the lower flange 53 is e, that is, equal to the eccentric amount of the eccentric portion 11.
Optionally, a first assembly gap is provided between the crankshaft 10 and the flange 50, the first assembly gap being in the range of 0.005mm to 0.05mm.
Preferably, the first assembly gap ranges from 0.01 to 0.03mm.
Alternatively, the two sliders 40 are respectively arranged concentrically with the two eccentric portions 11, the sliders 40 do circular motion around the axis of the crankshaft 10, and a first rotation gap is formed between the wall of the through hole 41 and the eccentric portions 11, and the range of the first rotation gap is 0.005 mm-0.05 mm.
As shown in fig. 2, 3, 6, 9 and 12, the shaft body portion 12 of the crankshaft 10 is integrally formed, and the shaft body portion 12 has only one axial center. Thus, the one-time molding of the shaft body part 12 is facilitated, and the processing and manufacturing difficulty of the shaft body part 12 is reduced.
In an embodiment of the present application, the shaft portion 12 of the crankshaft 10 includes a first section and a second section connected along an axial direction thereof, the first section and the second section are coaxially disposed, and the two eccentric portions 11 are disposed on the first section and the second section, respectively.
Optionally, the first section is detachably connected to the second section. In this way, convenience in assembling and disassembling the crankshaft 10 is ensured.
As shown in fig. 2, 3, 6, 9 and 12, the shaft body portion 12 of the crankshaft 10 is integrally formed with the eccentric portion 11. Thus, the crankshaft 10 is formed at one time, and the difficulty in machining and manufacturing the crankshaft 10 is reduced.
In an embodiment of the present application, not shown, the shaft portion 12 of the crankshaft 10 is detachably connected to the eccentric portion 11. In this way, the installation and the removal of the eccentric portion 11 are facilitated.
As shown in fig. 3 and 5, both ends of the stopper passage 31 penetrate to the outer peripheral surface of the intersecting groove structure 30. Thus, the difficulty in manufacturing the cross groove structure 30 is advantageously reduced.
It should be noted that, in the present application, the first included angle a is 160 degrees to 200 degrees; the second included angle B is 80-100 degrees. In this way, the relationship that the first angle a is twice the second angle B is satisfied.
Preferably, the first included angle a is 160 degrees and the second included angle B is 80 degrees.
Preferably, the first included angle a is 165 degrees and the second included angle B is 82.5 degrees.
Preferably, the first included angle a is 170 degrees and the second included angle B is 85 degrees.
Preferably, the first included angle a is 175 degrees and the second included angle B is 87.5 degrees.
Preferably, the first included angle a is 180 degrees and the second included angle B is 90 degrees.
Preferably, the first included angle a is 185 degrees and the second included angle B is 92.5 degrees.
Preferably, the first included angle a is 190 degrees and the second included angle B is 95 degrees.
Preferably, the first included angle a is 195 degrees and the second included angle B is 97.5 degrees.
In the present application, the eccentric portion 11 has an arc surface, and the central angle of the arc surface is 180 degrees or more. In this way, the arc surface of the eccentric portion 11 is ensured to be able to exert an effective driving force on the slider 40, thereby ensuring the movement reliability of the slider 40.
As shown in fig. 2, 3, 6, 9 and 12, two eccentric portions 11 are provided at intervals in the axial direction of the crankshaft 10. In this way, ensuring the separation distance between the two eccentric portions 11 during the assembly of the crankshaft 10, the cylinder liner 20 and the two sliders 40 can provide an assembly space for the cylinder liner 20 to ensure assembly convenience.
As shown in fig. 3, 5 and 8, the cross groove structure 30 has a center hole 32, two limiting passages 31 communicate through the center hole 32, and the diameter of the center hole 32 is larger than the diameter of the shaft body portion 12 of the crankshaft 10. In this way, it is ensured that the crankshaft 10 can pass smoothly through the center hole 32.
Alternatively, the bore diameter of the central bore 32 is larger than the diameter of the eccentric 11. In this way, it is ensured that the eccentric portion 11 of the crankshaft 10 can smoothly pass through the center hole 32.
As shown in fig. 13, the projection of the slider 40 in the axial direction of the through hole 41 has two relatively parallel straight line segments and an arc segment connecting the ends of the two straight line segments. The limiting channel 31 has a set of oppositely disposed first sliding surfaces in sliding contact with the slider 40, the slider 40 has a second sliding surface cooperating with the first sliding surfaces, the slider 40 has a pressing surface 42 facing the end of the limiting channel 31, the pressing surface 42 acts as the head of the slider 40, the two second sliding surfaces are connected by the pressing surface 42, and the pressing surface 42 faces the variable volume chamber 311. In this way, the projection of the second sliding surface of the slider 40 in the axial direction of the through hole 41 thereof is a straight line segment, while the projection of the pressing surface 42 of the slider 40 in the axial direction of the through hole 41 thereof is an arc segment.
Specifically, the pressing surface 42 is an arc surface, and the distance between the arc center of the arc surface and the center of the through hole 41 is equal to the eccentric amount of the eccentric portion 11. In FIG. 13, the center of the through hole 41 of the slider 40 is O Sliding block The distances between the centers of the two cambered surfaces and the center of the through hole 41 are e, that is, the eccentric amount of the eccentric portion 11, and the broken line X in fig. 13 indicates the circle in which the centers of the two cambered surfaces are located.
Alternatively, the radius of curvature of the arcuate surface is equal to the radius of the inner circle of the liner 20.
Alternatively, the radius of curvature of the arcuate surface has a difference from the radius of the inner circle of the liner 20 in the range of-0.05 mm to 0.025mm.
Preferably, the difference ranges from-0.02 to 0.02mm.
In the present application, the projected area S of the pressing surface 42 in the sliding direction of the slider 40 Sliding block Area S of the compression exhaust port 22 with the cylinder liner 20 Row of rows The following are satisfied: s is S Sliding block /S Row of rows The value of (2) is 8 to 25.
Preferably S Sliding block /S Row of rows The value of (2) is 12 to 18.
It should be noted that, the fluid machine shown in this embodiment is a compressor, as shown in fig. 1, the compressor includes a dispenser member 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, where the dispenser member 80 is disposed 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, and 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 compressor includes the crankshaft 10, cylinder liner 20, cross-slot structure 30, slide 40, upper flange 52 and lower flange 53 described above.
Optionally, the above components are connected by welding, hot sheathing, or cold pressing.
The entire pump body assembly 83 is assembled as follows: the lower flange 53 is fixed on the cylinder sleeve 20, the two sliding blocks 40 are respectively placed in the corresponding two limiting channels 31, the two eccentric parts 11 of the crankshaft 10 respectively extend into the two through holes 41 of the corresponding two sliding blocks 40, the assembled crankshaft 10, the cross groove structure 30 and the two sliding blocks 40 are placed in the cylinder sleeve 20, one end of the crankshaft 10 is mounted on the lower flange 53, and the other end of the crankshaft 10 is arranged through the upper flange 52, and particularly, see fig. 2 and 3.
It should be noted that, in the present embodiment, the enclosed space enclosed by the slide block 40, the limiting channel 31, the cylinder liner 20 and the upper flange 52 (or the lower flange 53) is the variable volume cavity 311, the pump body assembly 83 has 4 variable volume cavities 311 altogether, in the process of rotating the crankshaft 10, the crankshaft 10 rotates 2 circles, and a single variable volume cavity 311 completes 1 air intake and exhaust process, and for the compressor, the crankshaft 10 rotates 2 circles to complete 4 air intake and exhaust processes in total.
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, the partial inner wall surface of the cylinder liner 20, and the partial surface of the upper flange 52 facing the cylinder liner 20 (or the partial surface of the lower flange 53 facing the cylinder liner 20) is the variable volume cavity 311.
As shown in fig. 14 to 19, the slider 40 rotates relative to the cylinder liner 20 while reciprocating in the limiting passage 31, in fig. 14 to 16, the variable volume chamber 311 increases in the process of rotating the slider 40 clockwise from 0 degrees to 180 degrees, the variable volume chamber 311 communicates with the suction chamber 23 of the cylinder liner 20 in the process of increasing the variable volume chamber 311, when the slider 40 rotates to 180 degrees, the volume of the variable volume chamber 311 reaches the maximum value, the variable volume chamber 311 is separated from the suction chamber 23 at this time, thereby completing the suction operation, in fig. 17 to 19, the variable volume chamber 311 decreases in the process of continuing to rotate the slider 40 clockwise from 180 degrees to 360 degrees, the slider 40 compresses the gas in the variable volume chamber 311, when the slider 40 rotates to the variable volume chamber 311 communicates with the compression exhaust port 22, and when the gas in the variable volume chamber 311 reaches the exhaust pressure, the exhaust valve plate of the exhaust valve assembly 60 opens, and the exhaust operation starts until the next cycle is entered after the compression is completed.
As shown in fig. 14 to 19, with the point marked M as the reference point for the relative movement of the slide block 40 and the crankshaft 10, fig. 15 shows a process in which the slide block 40 rotates clockwise from 0 degrees to 180 degrees, the slide block 40 rotates at an angle θ1, the corresponding crankshaft 10 rotates at an angle 2θ1, fig. 17 shows a process in which the slide block 40 continues to rotate clockwise from 180 degrees to 360 degrees, the slide block 40 rotates at an angle 180 ° +θ2, the corresponding crankshaft 10 rotates at an angle 360 ° +2θ2, fig. 18 shows a process in which the slide block 40 continues to rotate clockwise from 180 degrees to 360 degrees, and the variable volume chamber 311 communicates with the compression exhaust port 22, the slide block 40 rotates at an angle 180 ° +θ3, the corresponding crankshaft 10 rotates at an angle 360 ° +2θ3, that is, the slide block 40 rotates 1 turn, and the corresponding crankshaft 10 rotates 2 turns, where θ1 < θ2 < θ3.
Specifically, as shown in fig. 14 to 19, the cylinder liner 20 has a compression intake port 21 and a compression exhaust port 22, and when any one of the sliders 40 is in the intake position, the compression intake port 21 is in communication with the corresponding volume chamber 311; when any one of the sliders 40 is in the discharge position, the corresponding volume chamber 311 is in communication with the compression discharge port 22.
As shown in fig. 14 to 19, the inner wall surface of the cylinder liner 20 has a suction chamber 23, and the suction chamber 23 communicates with the compression intake 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 be filled with suction gas, thereby enabling the compressor to be capable of sucking gas in a sufficient amount, and when the suction gas is insufficient, the stored gas can be timely supplied to the variable volume chamber 311, so as to ensure the compression efficiency of the compressor.
Alternatively, the suction chambers 23 are cavities formed by hollowing out the inner wall surface of the cylinder sleeve 20 along the radial direction, and the number of the suction chambers 23 can be 1 or 2.
Specifically, the suction chamber 23 extends a first preset distance around the circumference of the inner wall surface of the cylinder liner 20 to constitute an arc-shaped suction chamber 23. In this way, it is ensured that the volume of the suction chamber 23 is sufficiently large to store a large amount of gas.
As shown in fig. 10, the number of the suction chambers 23 is two, the two suction chambers 23 are arranged at intervals along the axial direction of the cylinder sleeve 20, the cylinder sleeve 20 is also provided with a suction communication chamber 24, the two suction chambers 23 are communicated with the suction communication chamber 24, and the compression air inlet 21 is communicated with the suction chamber 23 through the suction communication chamber 24. In this way, it is advantageous to increase the volume of the suction chamber 23, thereby reducing suction pressure pulsation.
As shown in fig. 2, the suction communication chamber 24 extends a second predetermined distance in the axial direction of the cylinder liner 20, and at least one end of the suction communication chamber 24 penetrates through the axial end face of the cylinder liner 20. Thus, the air suction communication cavity 24 is conveniently formed on the end face of the cylinder sleeve 20, and the processing convenience of the air suction communication cavity 24 is ensured.
As shown in fig. 10, 14-19, the outer wall of the cylinder sleeve 20 is provided with an exhaust cavity 25, the compression 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 60, wherein the exhaust valve assembly 60 is arranged in the exhaust cavity 25 and corresponds to the compression exhaust port 22. In this way, the exhaust cavity 25 is used for accommodating the exhaust valve assembly, so that the occupied space of the exhaust valve assembly is effectively reduced, components are reasonably arranged, and the space utilization rate of the cylinder sleeve 20 is improved.
As shown in fig. 10, 14 to 19, there are two compression exhaust ports 22, two compression exhaust ports 22 are arranged at intervals along the axial direction of the cylinder liner 20, two exhaust valve assemblies are arranged, and two exhaust valve assemblies are respectively arranged corresponding to the two compression exhaust ports 22. In this way, since the two compression exhaust ports 22 are respectively provided with two groups of exhaust valve assemblies, a great amount of gas in the variable-volume cavity 311 is effectively prevented from leaking, and the compression efficiency of the variable-volume cavity 311 is ensured.
It should be noted that, in the present application, the exhaust valve assembly is connected to the cylinder liner 20 through the fastener 90, and the exhaust valve assembly includes an exhaust valve plate and a valve plate baffle, where the exhaust valve plate is disposed in the exhaust cavity 25 and shields the corresponding compressed exhaust port 22, and the valve plate baffle is disposed on the exhaust valve plate in an overlapping manner. In this way, the valve block baffle is arranged, so that the transition opening of the exhaust valve block is effectively avoided, and the exhaust performance of the cylinder sleeve 20 is ensured.
Alternatively, the fastener 90 is a screw.
As shown in fig. 10, 13 and 18 to 20, the axial end face of the cylinder liner 20 is further provided with a communication hole, the communication hole is communicated with the exhaust chamber 25, the fluid machine further comprises a flange 50, an exhaust passage is provided on the flange 50, and the communication hole is communicated with the exhaust passage. In this way, the exhaust reliability of the cylinder liner 20 is ensured.
As shown in fig. 20, the exhaust chamber 25 penetrates through the outer wall surface of the cylinder liner 20, and the fluid machine further includes an exhaust cover plate 70, and the exhaust cover plate 70 is connected with the cylinder liner 20 and seals the exhaust chamber 25. In this way, the vent cover plate 70 functions to isolate the variable volume chamber 311 from the external space of the pump body assembly 83.
As shown in fig. 18 and 19, when the pressure of the variable volume chamber 311 reaches the discharge pressure after the variable volume chamber 311 is communicated with the compression discharge port 22, the discharge valve plate is opened, and the compressed gas enters the discharge chamber 25 through the compression discharge port 22, passes through the communication hole on the cylinder liner 20, is discharged through the discharge passage, and enters the external space of the pump body assembly 83 (i.e., the chamber of the compressor), thereby completing the discharge process.
Optionally, the exhaust cover plate 70 is secured to the cylinder liner 20 by fasteners 90.
Alternatively, the fastener 90 is a screw.
Optionally, the outer contour of the vent flap 70 is adapted to the outer contour of the vent chamber 25.
The operation of the compressor is described in detail below:
as shown in fig. 1, the motor assembly 82 drives the crankshaft 10 to rotate, two eccentric parts 11 of the crankshaft 10 respectively drive two corresponding sliding blocks 40 to move, the sliding blocks 40 revolve around the axis of the crankshaft 10 and simultaneously, the sliding blocks 40 rotate relative to the eccentric parts 11, the sliding blocks 40 reciprocate along the limiting channels 31 and drive the cross groove structure 30 to rotate in the cylinder sleeve 20, and the sliding blocks 40 revolve and simultaneously reciprocate along the limiting channels 31 to form a cross sliding block mechanism movement mode.
Other use occasions: the compressor can be used as an expander by exchanging positions of the suction port and the exhaust port. That is, the high-pressure gas is introduced into the exhaust port of the compressor as the intake port of the expander, and the other pushing mechanism rotates, and the gas is discharged through the intake port of the compressor (the exhaust port of the expander) after expansion.
When the fluid machine is an expander, the cylinder sleeve 20 is provided with an expansion exhaust port and an expansion air inlet, and when any slide block 40 is positioned at the air inlet position, the expansion exhaust port is communicated with the corresponding volume cavity 311; when any one of the sliders 40 is in the exhaust position, the corresponding volume chamber 311 is in communication with the expansion intake port. Thus, when the high-pressure gas enters the variable volume cavity 311 through the expansion air inlet, the high-pressure gas pushes the cross groove structure 30 to rotate, the cross groove structure 30 rotates to drive the sliding block 40 to rotate, and simultaneously the sliding block 40 slides linearly relative to the cross groove structure 30, so that the sliding block 40 drives the eccentric part 11 to rotate, that is, drives the crankshaft 10 to rotate. By connecting the crankshaft 10 to other power consuming devices, work can be output from the crankshaft 10.
Optionally, the inner wall surface of the cylinder liner 20 has an expansion exhaust chamber in communication with the expansion exhaust port.
Further, the expansion exhaust chamber extends around the circumference of the inner wall surface of the cylinder liner 20 by a first preset distance to form an arc expansion exhaust chamber, and the expansion exhaust chamber extends from the expansion exhaust port to the side where the expansion air inlet is located, and the extending direction of the expansion exhaust chamber is in the same direction as the rotating direction of the cross groove structure 30.
Further, two expansion exhaust chambers are arranged at intervals along the axial direction of the cylinder sleeve 20, the cylinder sleeve 20 is further provided with expansion exhaust communication chambers, the two expansion exhaust chambers are communicated with the expansion exhaust communication chambers, and the expansion exhaust ports are communicated with the expansion exhaust chambers through the expansion exhaust communication chambers.
Further, the expansion exhaust communication chamber extends a second preset distance along the axial direction of the cylinder liner 20, and at least one end of the expansion exhaust communication chamber penetrates through the axial end surface of the cylinder liner 20.
For the problem of how to ensure that the overall efficiency of the compressor is optimized, the following reasonably optimizes the first radial clearance C1 between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder liner 20, specifically as follows:
the cross groove structure 30 and the cylinder sleeve 20 are coaxially arranged, a first radial clearance C1 is formed between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder sleeve 20, and the range of the first radial clearance C1 is 0.01-0.08 mm.
By applying the technical scheme of the invention, based on the principle of optimal comprehensive efficiency of the compressor, the radial dimension relation of the pump body component of the compressor is defined, and scheme optimization is carried out aiming at each design variable influencing the radial dimension, so that the mechanical efficiency and the volumetric efficiency of the compressor are ensured to be in a better range, and the optimal comprehensive energy efficiency of the compressor is ensured.
Further, considering that the first radial clearance C1 between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder sleeve 20 is filled with lubricating oil during the operation of the compressor, the lubricating mode between the cross groove structure 30 and the cylinder sleeve 20 is hydrodynamic lubrication, and under the hydrodynamic lubrication mode, the larger the clearance is, the larger the friction power consumption is, and the higher the mechanical efficiency of the compressor is; meanwhile, during the operation of the compressor, the air at the end portions of the sliding block 40 at both sides in the sliding direction has a pressure difference, the side communicated with the air suction channel is air suction pressure, the other end is intermediate pressure or air discharge pressure in the compression process, the air leaks from the high pressure side to the low pressure side through the first radial clearance C1 between the cross groove structure 30 and the cylinder sleeve 20, the smaller the clearance at the low pressure side is, the better the tightness is, the smaller the leakage is, and the volumetric efficiency of the compressor is higher.
In summary, the influence of the first radial clearance C1 on the mechanical efficiency and the volumetric efficiency is opposite, and theoretical analysis and experimental verification prove that the range of the first radial clearance C1 is reasonably optimized, so that the first radial clearance C1 is positioned in the range of 0.01-0.08 mm, and the comprehensive efficiency of the compressor can be improved.
Table 1 effect of first radial clearance C1 on respective efficiency of compressor
As is clear from table 1 and fig. 26, the overall efficiency of the compressor is optimal when the first radial clearance C1 is in the range of 0.015 to 0.03 mm.
It should be noted that, during the assembly of the pump body assembly 83, the eccentric portion 11 of the crankshaft 10 needs to pass through the central hole 32, and, considering that the larger the diameter of the eccentric portion 11 is, the larger the outer circle diameter of the cross groove structure 30 is, the larger the mechanical power consumption of the whole machine is, therefore, the aperture of the central hole 32 is larger than the diameter of the eccentric portion 11, and the second radial clearance C2 is provided between the wall surface of the central hole 32 and the outer peripheral surface of the eccentric portion 11, and as can be seen from table 2 and fig. 27, the mechanical efficiency of the compressor is higher when the range of the second radial clearance C2 is 0.05-1 mm. In this way, by reasonably optimizing the second radial clearance C2 between the wall surface of the central hole 32 and the outer peripheral surface of the eccentric portion 11, the second radial clearance C2 is made as small as possible on the premise that the eccentric portion 11 can smoothly pass through the central hole 32.
TABLE 2 influence of the second radial clearance C2 on the mechanical efficiency of the compressor
As shown in fig. 4 and 5, the inner diameter D of the cylinder liner 20 Cylinder sleeve Diameter d of outer circle of cross groove structure 30 Groove(s) The following are satisfied: d (D) Cylinder sleeve ＝d Groove(s) +2c1; hole diameter D of center hole 32 Limiting the limit Diameter d of eccentric portion 11 Offset of deflection The following are satisfied: d (D) Limiting the limit ＝d Offset of deflection +2C2。
It should be noted that, during the operation of the compressor, the inner cavity of the cross groove structure 30 is in a high pressure state, during the air suction stage, the pressure in the variable volume cavity 311 is an air suction pressure, and is in a low pressure state, during the compression, the pressure in the variable volume cavity 311 gradually increases, and is in an intermediate pressure state that is greater than the air suction pressure and less than the air discharge pressure, after reaching the air discharge pressure, the compressor enters the air discharge stage, and the pressure in the variable volume cavity 311 keeps the air discharge pressure (high pressure) unchanged during the air discharge.
As shown in fig. 3, 8 and 9, the slider 40 has a pressing surface 42 toward the end of the restricting passage 31, the pressing surface 42 being the head of the slider 40, the pressing surface 42 being directed toward the variable volume chamber 311; the pressing surface 42 is a cambered surface, a sealing distance M is provided between the top end of the cambered surface and the wall surface of the central hole 32, and the sealing distance M periodically changes along with the sliding of the sliding block 40 in the limiting channel 31.
Further, during the suction and compression processes, the pressure in the inner cavity of the cross groove structure 30 is higher than the pressure in the variable volume cavity 311, and a certain leakage exists under the action of the pressure difference, and the leakage is inversely proportional to the sealing distance M, that is, the larger the sealing distance M, the smaller the leakage.
Specifically, when the pump body assembly 83 is at 180 ° (i.e., the suction is completed), the sealing distance M is minimum, and the pressure difference across the leakage path is maximum at this position, the leakage is also maximum at this time, and the larger the sealing distance M, the larger the outside diameter of the cross groove structure 30 is, the friction power consumption of the compressor is, and it can be seen that the influence of the sealing distance M on the volumetric efficiency and mechanical efficiency of the compressor is opposite, and there is an optimum interval.
Further, the sealing distance M has a minimum sealing distance M Minimum of Minimum seal distance M Minimum of The range of (2) is 1-6 mm.
TABLE 3 minimum seal distance M Minimum of Effects on efficiency of compressor
| Minimum sealing distance M Minimum of | 1mm | 2mm | 3mm | 4mm | 5mm | 6mm |
| Mechanical efficiency | 93.3％ | 92.7％ | 91.8％ | 90.0％ | 88.2％ | 85.3％ |
| Volumetric efficiency | 88.5％ | 91.3％ | 91.5％ | 91.7％ | 92.2％ | 93.2％ |
| Comprehensive efficiency | 82.6％ | 84.6％ | 84.0％ | 82.5％ | 81.3％ | 79.5％ |
Further, as can be seen from a combination of Table 3 and FIG. 28, the minimum seal distance M Minimum of When the range is 2-4 mm, the comprehensive efficiency of the compressor is higher.
In the present application, the seal distance M has the minimum seal distance M Minimum of Outer diameter d of cross groove structure 30 Groove(s) Hole diameter D of center hole 32 Limiting the limit The eccentricity e of the eccentric portion 11 satisfies: d, d Groove(s) ＝D Limiting the limit +8e+2M Minimum of 。
As shown in fig. 6 and 7, the eccentric portion 11 has a cylindrical shape, and a proximal end of the eccentric portion 11 protrudes from an outer circumference of a shaft portion of the crankshaft 10.
It should be noted that, during the assembly of the pump body assembly 83, the shaft body portion 12 of the crankshaft 10 passes through the through hole 41 of the slider 40 first, and then the eccentric portion 11 of the crankshaft 10 passes through the through hole 41, and during this process, any position of the outer circle of the eccentric portion 11 of the crankshaft 10 needs to protrude the outer circle of the shaft body portion 12, that is, the protruding amount T of the proximal end of the eccentric portion 11 satisfies: t > 0, otherwise normal assembly cannot be completed, and the position where the protruding amount Tmin is where the proximal end of the eccentric portion 11 protrudes from the outer circumference of the shaft body portion 12 of the crankshaft 10.
TABLE 4 influence of minimum protrusion T on mechanical efficiency of compressor
Preferably, as can be seen from table 4 and fig. 29, the mechanical efficiency of the compressor is high when the protrusion amount T of the proximal end of the eccentric portion 11 is in the range of 0.1 to 2 mm.
As shown in fig. 6 and 7, d Offset of deflection /2＝e+d Shaft 2+T, where d Offset of deflection Is the diameter d of the eccentric part 11 Shaft E is the eccentric amount of the eccentric portion 11, and T is the protruding amount of the proximal end of the eccentric portion 11, which is the diameter of the shaft body portion 12.
Further, the protrusion T of the proximal end of the eccentric portion 11, the diameter d of the eccentric portion 11 Offset of deflection Diameter d of shaft body part Shaft The eccentricity e of the eccentric portion 11 satisfies: d, d Offset of deflection ＝d Shaft +2e+2T。
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present application unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.
Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
It should be noted that the terms "first," "second," and the like in the description and the claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that embodiments of the application described herein may be implemented in sequences other than those illustrated or otherwise described herein.
The above description is only of the preferred embodiments of the present application and is not intended to limit the present application, but various modifications and variations can be made to the present application by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the protection scope of the present application.
Claims (15)
1. A fluid machine, comprising:
a crankshaft (10), the crankshaft (10) being provided with two eccentric portions (11) along its axial direction;
the crankshaft (10) and the cylinder sleeve (20) are eccentrically arranged, and the eccentric distance is fixed;
the cross groove structure (30) is rotatably arranged in the cylinder sleeve (20), the cross groove structure (30) and the cylinder sleeve (20) are coaxially arranged, a first radial clearance C1 is formed between the outer peripheral surface of the cross groove structure (30) and the inner wall surface of the cylinder sleeve (20), the range of the first radial clearance C1 is 0.01-0.08 mm, the cross groove structure (30) is provided with two limiting channels (31), the two limiting channels (31) are sequentially arranged along the axial direction of the crankshaft (10), and the extending direction of the limiting channels (31) is perpendicular to the axial direction of the crankshaft (10);
The sliding block (40), the sliding block (40) has through-hole (41), the sliding block (40) is two, two eccentric part (11) correspond to stretch into two in the through-hole (41) of two sliding block (40), two sliding block (40) correspond the slip setting in two spacing passageway (31) and form variable volume chamber (311), variable volume chamber (311) are located the slip direction of sliding block (40), bent axle (10) rotate in order to drive sliding block (40) in spacing passageway (31) reciprocal slip simultaneously with cross groove structure (30) interact, make cross groove structure (30) slider (40) are in cylinder liner (20) internal rotation.
2. The fluid machine of claim 1, wherein the first radial clearance C1 ranges from 0.015 to 0.03mm.
3. The fluid machine according to claim 1, characterized in that the cross-slot structure (30) has a central bore (32), through which central bore (32) two of the limiting channels (31) communicate, the bore diameter of the central bore (32) being larger than the diameter of the shaft body part (12) of the crankshaft (10).
4. A fluid machine according to claim 3, wherein the bore diameter of the central bore (32) is larger than the diameter of the eccentric portion (11), a second radial clearance C2 is provided between the bore wall surface of the central bore (32) and the outer circumferential surface of the eccentric portion (11), the second radial clearance C2 being in the range of 0.05-1 mm.
5. The fluid machine according to claim 4, wherein the fluid machine is further configured to,
the inner diameter D of the cylinder sleeve (20) Cylinder sleeve Diameter d of the outer circle of the cross groove structure (30) Groove(s) The following are satisfied: d (D) Cylinder sleeve ＝d Groove(s) +2C1；
Hole diameter D of the center hole (32) Limiting the limit Diameter d with the eccentric part (11) Offset of deflection The following are satisfied: d (D) Limiting the limit ＝d Offset of deflection +2C2。
6. A fluid machine according to claim 3, wherein,
the sliding block (40) is provided with a pressing surface (42) facing the end part of the limiting channel (31), the pressing surface (42) is used as the head part of the sliding block (40), and the pressing surface (42) faces the variable volume cavity (311);
the extrusion surface (42) is a cambered surface, a sealing distance M is arranged between the top end of the cambered surface and the hole wall surface of the central hole (32), and the sealing distance M periodically changes along with the sliding of the sliding block (40) in the limiting channel (31).
7. The fluid machine of claim 6, wherein the seal distance M has a minimum seal distance M Minimum of The minimum sealing distance M Minimum of The range of (2) is 1-6 mm.
8. The fluid machine of claim 7, wherein the minimum seal distance M Minimum of The range of (2) to (4) mm.
9. The fluid machine of claim 6, wherein the seal distance M has a minimum seal distance M Minimum of The outer circle diameter d of the cross groove structure (30) Groove(s) Hole diameter D of the center hole (32) Limiting the limit The eccentric amount e of the eccentric part (11) satisfies: d, d Groove(s) ＝D Limiting the limit +8e+2M Minimum of 。
10. The fluid machine according to claim 1, characterized in that the eccentric portion (11) is cylindrical, the proximal end of the eccentric portion (11) protruding from the outer circumference of the shaft body portion (12) of the crankshaft (10).
11. The fluid machine according to claim 10, characterized in that the protrusion T of the proximal end of the eccentric portion (11) satisfies: t > 0.
12. The fluid machine according to claim 11, characterized in that the protrusion T of the proximal end of the eccentric portion (11) ranges from 0.1 to 2mm.
13. The fluid machine according to claim 10, characterized in that the protrusion T of the proximal end of the eccentric portion (11), the diameter d of the eccentric portion (11) Offset of deflection Diameter d of the shaft body part (12) Shaft The eccentric amount e of the eccentric part (11) satisfies: d, d Offset of deflection ＝d Shaft +2e+2T。
14. The fluid machine according to any one of claims 1 to 13, characterized in that the two eccentric portions (11) have a phase difference of a first angle a, the eccentric amounts of the two eccentric portions (11) are equal, and the two limiting channels (31) have a phase difference of a second angle B in the extending direction, wherein the first angle a is twice the second angle B.
15. A heat exchange device comprising a fluid machine, characterized in that the fluid machine is a fluid machine according to any one of claims 1 to 14.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210565498.0A CN117145770A (en) | 2022-05-23 | 2022-05-23 | Fluid machine and heat exchange device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210565498.0A CN117145770A (en) | 2022-05-23 | 2022-05-23 | Fluid machine and heat exchange device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117145770A true CN117145770A (en) | 2023-12-01 |
Family
ID=88885454
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210565498.0A Pending CN117145770A (en) | 2022-05-23 | 2022-05-23 | Fluid machine and heat exchange device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117145770A (en) |
-
2022
- 2022-05-23 CN CN202210565498.0A patent/CN117145770A/en active Pending
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP6496452B2 (en) | Fluid machine, heat exchange device and method of operating fluid machine | |
| CN107152392B (en) | Pump body assembly, fluid machine and heat exchange equipment | |
| WO2017024866A1 (en) | Compressor, heat exchanging apparatus, and operating method for compressor | |
| WO2017024868A1 (en) | Fluid machinery, heat exchange device, and method for operating fluid machinery | |
| WO2017024862A1 (en) | Fluid machine, heat exchanger, and operating method of fluid machine | |
| CN103821715A (en) | Translational rotation type compression machinery | |
| CN216381861U (en) | Pump body assembly and enthalpy-increasing rotor compressor | |
| CN117145770A (en) | Fluid machine and heat exchange device | |
| WO2023097898A1 (en) | Pump assembly and enthalpy-increasing rotor compressor | |
| CN206592288U (en) | Rotary compressor | |
| CN117145765A (en) | Fluid machine and heat exchange device | |
| CN114320822A (en) | Rotary piston compressor | |
| CN117145769A (en) | Fluid machine and heat exchange device | |
| WO2023103876A1 (en) | Fluid machinery and heat exchange device | |
| CN116241466A (en) | Fluid machine, heat exchange device, and method for operating a fluid machine | |
| CN117145773A (en) | Fluid machine and heat exchange device | |
| WO2023226413A1 (en) | Fluid machine and heat exchange device | |
| CN116241472A (en) | Fluid machine and heat exchange device | |
| CN116241465A (en) | Fluid machine, heat exchange device and method for operating a fluid machine | |
| CN117145771A (en) | Fluid machine and heat exchange device | |
| CN117145768A (en) | Fluid machine and heat exchange device | |
| CN117145767A (en) | Fluid machine and heat exchange device | |
| CN116241467A (en) | Fluid machine and heat exchange device with bearing | |
| CN117145766A (en) | Fluid machine and heat exchange device | |
| WO2023103872A1 (en) | Fluid machinery, heat exchange apparatus, and operation method for fluid machinery |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication |