CN117145766A - Fluid machine and heat exchange device - Google Patents
Fluid machine and heat exchange device Download PDFInfo
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- CN117145766A CN117145766A CN202210563914.3A CN202210563914A CN117145766A CN 117145766 A CN117145766 A CN 117145766A CN 202210563914 A CN202210563914 A CN 202210563914A CN 117145766 A CN117145766 A CN 117145766A
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- fluid machine
- crankshaft
- suction
- exhaust
- cylinder sleeve
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- 239000012530 fluid Substances 0.000 title claims abstract description 47
- 238000004891 communication Methods 0.000 claims description 20
- 230000000149 penetrating effect Effects 0.000 claims 1
- 238000012545 processing Methods 0.000 abstract description 13
- 230000009467 reduction Effects 0.000 abstract description 2
- 230000007246 mechanism Effects 0.000 description 19
- 238000000034 method Methods 0.000 description 11
- 238000007906 compression Methods 0.000 description 9
- 238000010586 diagram Methods 0.000 description 9
- 238000003825 pressing Methods 0.000 description 8
- 230000006835 compression Effects 0.000 description 7
- 230000008569 process Effects 0.000 description 6
- 230000009286 beneficial effect Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 230000014509 gene expression 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
- 238000005457 optimization Methods 0.000 description 1
- 238000005498 polishing Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
-
- 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
-
- 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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
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, a sliding block and two flanges, wherein 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, and two limiting channels of the cross groove structure are sequentially arranged along the axial direction of the crankshaft; the two eccentric parts correspondingly extend into two through holes of the two sliding blocks, the two sliding blocks are correspondingly arranged in the two limiting channels in a sliding manner and form a variable volume cavity, and the variable volume cavity is positioned in the sliding direction of the sliding blocks; the two flanges are provided with exhaust channels which are respectively communicated with the variable volume cavities at the corresponding sides; wherein the cross-sectional area of the passage section of the exhaust passage is 0.5% -35% of the projected area of the slider in the sliding direction thereof. The invention solves the problems of low energy efficiency, high noise, and reduction of the processing difficulty of the exhaust port, the clearance volume and the noise 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, most of the existing compressors perform side exhaust through the side wall surface of the cylinder sleeve, an exhaust port on the cambered surface is not well opened in the processing of parts, and the clearance volume caused by the side exhaust is large, and large noise exists.
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 reduction of the processing difficulty of an exhaust port and the clearance volume and noise 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, a slider, and two flanges, the crankshaft being 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 and 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 blocks are provided with through holes, 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 way to form a variable-volume cavity, the variable-volume cavity is positioned in the sliding direction of the sliding blocks, and the crankshaft rotates to drive the sliding blocks to reciprocally slide in the limiting channels and interact with the cross groove structure, so that the cross groove structure and the sliding blocks rotate in the cylinder sleeve; the two flanges are respectively arranged at the two axial ends of the cylinder sleeve, exhaust channels are respectively arranged on the two flanges, and the two exhaust channels are respectively communicated with the variable volume cavities at the corresponding sides; wherein the cross-sectional area of the passage section of the exhaust passage is 0.5% -35% of the projected area of the slider in the sliding direction thereof.
Further, the projection of the slider in the sliding direction thereof is semicircular.
Further, the projection of the sliding block in the axial direction of the through hole is provided with two relatively parallel straight line sections and an arc line section connecting the end parts of the two straight line sections; the arrangement position of the exhaust passage in the circumferential direction of the flange is in the angle range of (90 ° -arccos (C/D) to 90 ° + arccos (C/D)), wherein C is the distance between two relatively parallel straight line segments of the projection of the slider in the axial direction of the through hole, and D is the inner diameter of the cylinder liner.
Further, oblique cuts are formed in the edges of the inner circles at the two axial ends of the cylinder sleeve, and the two oblique cuts are respectively communicated with the two exhaust channels.
Further, the two exhaust passages are concentrically arranged in the axial direction of the cylinder sleeve, and the two oblique cuts are consistent in position in the circumferential direction of the cylinder sleeve; or, the two exhaust passages are arranged in a non-concentric manner in the axial direction of the cylinder sleeve, and the positions of the two oblique cuts in the circumferential direction of the cylinder sleeve are not consistent.
Further, the sum of the projection area of the oblique notch on the inner circle of the cylinder sleeve and the projection area of the oblique notch on the end face of the cylinder sleeve is larger than or equal to the sectional area of the passage section of the exhaust passage.
Further, a drainage groove is formed in the end face, facing one side of the cylinder sleeve, of the flange, the drainage groove is communicated with the exhaust channel, and the drainage groove is arranged opposite to and communicated with the oblique notch.
Further, the cylinder sleeve is provided with at least one radial air suction hole, the radial air suction hole is used for being communicated with the variable-volume cavity, the inner wall surface of the cylinder sleeve is provided with an air suction cavity, and the radial air suction hole is communicated with the variable-volume cavity through the air suction cavity.
Further, the suction cavity extends a first preset distance around the circumference of the inner wall surface of the cylinder sleeve to form an arc-shaped suction cavity.
Further, the two air suction cavities are arranged at intervals along the axial direction of the cylinder sleeve, the cylinder sleeve is further provided with an air suction communication cavity, the two air suction cavities are communicated with the air suction communication cavity, and when the cylinder sleeve is provided with a radial air suction hole, the radial air suction hole is communicated with the two air suction cavities through the air suction communication cavity.
Further, the air suction communication cavity extends for a second preset distance along the axial direction of the cylinder sleeve, and at least one end of the air suction communication cavity penetrates through the axial end face of the cylinder sleeve.
Further, the number of the two air suction cavities is two, the two air suction cavities are arranged at intervals along the axial direction of the cylinder sleeve, the number of the two radial air suction holes is two, the two radial air suction holes are in one-to-one correspondence with the two air suction cavities, and the two radial air suction holes are respectively communicated with the corresponding volume cavities through the two air suction cavities.
Further, one of the two flanges is provided with an air inlet channel, the air inlet channel and the air outlet channel on the same flange are provided with phase differences in the circumferential direction of the flange, the cylinder sleeve is provided with a radial air suction hole, and the air inlet channel and the radial air suction hole are respectively communicated with the two variable-volume cavities.
Further, the two flanges are provided with air inlet channels, the air inlet channels and the air outlet channels on the same flange are provided with phase differences in the circumferential direction of the flange, and the two air inlet channels are respectively communicated with the two variable-volume cavities.
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 adopting the technical scheme, the two flanges are provided with the exhaust channels, and the two exhaust channels are respectively communicated with the variable volume chambers at the corresponding sides, so that compared with the existing exhaust channels which are arranged on the cambered surfaces of the side walls of the cylinder sleeve, the exhaust channels are arranged on the planes of the flanges, the exhaust channels are beneficial to reducing noise influence caused by the existence of edges of the exhaust channels, uneven assembly of the cylinder sleeve and the flange in the assembly process, and the like, and the exhaust path of the fluid machinery is changed to avoid noise; in addition, because the exhaust passage is arranged on the plane of the flange and belongs to the outer plane, compared with the exhaust passage arranged on the cambered surface of the side wall of the cylinder sleeve, the processing difficulty of the exhaust passage is greatly reduced, the processing of parts is relatively easier, and the flange or burr and the like caused by processing are facilitated to polish.
Further, because both ends in the length direction of the exhaust channel of the fluid machine are plane, the volume of the exhaust channel of the plane is smaller, the clearance volume is smaller, and the cooling capacity is guaranteed and the power consumption is reduced under the condition that the bearing thickness and the diameter of the exhaust channel are the same.
In addition, by reasonably optimizing the cross-sectional area of the passage section of the exhaust passage and the ratio of the projection area of the sliding block in the sliding direction, exhaust loss is avoided.
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 cross-sectional structural view of a first 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 diagram of the assembled structure of the crankshaft, cross slot structure, and slider of FIG. 3;
FIG. 5 shows a schematic cross-sectional view of the crankshaft, cross slot configuration, and slider of FIG. 4;
FIG. 6 shows a schematic cross-sectional structural view of a second view of the pump body assembly of the compressor of FIG. 1;
FIG. 7 shows a schematic cross-sectional structural view of the E-E view of FIG. 6;
FIG. 8 shows a schematic structural view of an alternative embodiment of the upper flange of the pump body assembly of FIG. 3;
FIG. 9 shows a schematic structural view of the upper flange of the pump body assembly of FIG. 3 with a drainage groove;
fig. 10 shows an enlarged schematic view of the structure at F in fig. 9;
FIG. 11 shows a schematic cross-sectional structural view of the upper flange of FIG. 9 at the vent channel and drain chute;
FIG. 12 shows a schematic structural view of an alternative embodiment of the lower flange of the pump body assembly of FIG. 3;
FIG. 13 shows a schematic view of the lower flange of the pump body assembly of FIG. 3 with a drainage groove;
fig. 14 shows an enlarged structural schematic diagram at G in fig. 13;
FIG. 15 shows a schematic cross-sectional structural view of the lower flange of FIG. 13 at the vent channel and drain chute;
FIG. 16 shows a schematic structural view of the vent passage of the upper flange of FIG. 3 in an angular position in the circumferential direction of the upper flange;
FIG. 17 is a schematic view showing the structure of the exhaust passage of the lower flange in FIG. 3 at an angular position in the circumferential direction of the lower flange;
FIG. 18 shows a schematic structural view of a cylinder liner of the pump body assembly of FIG. 3;
FIG. 19 shows a schematic view of the upper flange, cylinder liner, lower flange of the pump body assembly of FIG. 3 in an exploded condition;
FIG. 20 shows a schematic view of a cylinder liner single suction in a pump body structure according to a first embodiment of the present invention;
FIG. 21 shows a schematic diagram of a cylinder liner double suction structure of a pump body structure according to a second embodiment of the present invention;
FIG. 22 shows a schematic diagram of the suction of the upper and lower flanges of the pump body structure according to a third embodiment of the invention;
FIG. 23 shows a schematic view of a cylinder liner single suction fitting flange single suction of a pump body structure according to a fourth embodiment of the present invention;
FIG. 24 is a schematic view showing the structure of the shaft body portion and the eccentric amounts of the two eccentric portions of the crankshaft in FIG. 3;
FIG. 25 is a schematic cross-sectional structural view showing the amount of assembly eccentricity of the crankshaft and cylinder liner of FIG. 3;
FIG. 26 is a schematic view showing the structure of the eccentricity between the cylinder liner and the lower flange of FIG. 3;
FIG. 27 is a schematic view showing the structure of the slider in FIG. 3 in the axial direction of the through hole;
FIG. 28 illustrates a schematic mechanical diagram of the operation of a compressor in accordance with an alternative embodiment of the present invention;
FIG. 29 is a schematic diagram showing the principle of the mechanism of operation of the compressor of FIG. 28;
FIG. 30 is a schematic diagram illustrating the mechanism of operation of a prior art compressor;
FIG. 31 is a schematic diagram showing the mechanism principle of the compressor operation after improvement in the prior art;
FIG. 32 is a schematic diagram of the mechanism of operation of the compressor of FIG. 31 showing the moment arm of the drive shaft driving the slider in rotation;
fig. 33 shows a schematic view of the principle of the mechanism of operation of the compressor of fig. 31, in which the center of the limit groove structure and the center of the eccentric portion coincide.
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. radial suction holes; 23. an air suction cavity; 24. an air suction communication cavity; 27. oblique cuts;
30. a cross slot structure; 31. a limiting channel; 32. a central bore;
40. a slide block; 41. a through hole; 42. extruding the surface;
50. a flange; 51. an exhaust passage; 52. an upper flange; 53. a lower flange; 54. an air intake passage; 58. drainage grooves;
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. 30, 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. 31, 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 air cylinder is equal to the eccentric amount of the eccentric part, so that the sliding block slidesBlock 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. 32, 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 And an included angle between the connecting line and the sliding direction of the sliding block in the limiting groove.
As shown in FIG. 33, 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 the principle, the application provides a brand-new mechanism principle of a cross groove structure with two limiting channels and double sliding blocks, and a brand-new compressor is constructed based on the principle, and the compressor has the characteristics of high energy efficiency and low noise.
In order to solve the problems of low energy efficiency and high noise of the compressor in the prior art and how to reduce the processing difficulty of the exhaust port and reduce the clearance volume and the noise, the application 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 to form a variable-volume cavity, the variable-volume cavity is located 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, 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 eccentric part 11 with the maximum driving torque can normally drive the corresponding sliding block 40 to rotate, the cross groove structure 30 is driven to rotate through the sliding block 40, the sliding block 40 at the dead point position is driven to continuously rotate through the cross groove structure 30, the reliability of mechanical lifting and stability of the operation of the fluid is realized, and the reliability of the operation and the reliability of the fluid movement 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. 28 and 29, 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 between the two eccentric parts is equal to the eccentric amount of the first 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 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 cross-slide mechanism, which operates using the principle of a cross-slide mechanism, in which two deviations of the crankshaft 10 are usedThe core 11 is respectively used 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. 28).
As shown in fig. 28, 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. 29, 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 A fifth included angle E is formed between the two connecting rods, 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 thirdConnecting 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 The revolution, simultaneously the slider 40 can rotate relative to the eccentric part 11, and the relative rotation speed of the two sliders is the same, because the first slider 40 and the second slider 40 respectively reciprocate in the two corresponding limiting channels 31 and drive the cross groove structure 30 to do circular motion, the two limiting channels 31 of the cross groove structure 30 limit the motion direction of the two sliders 40 always have the 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 of the two sliders 40 has the maximum driving torque, and 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, further driving the slider 40 at the dead point position to continue to rotate through the cross groove structure 30, realizing the stable operation of the fluid machinery, avoiding the dead point position of the motion mechanism, improving the motion reliability of the fluid machinery, and thus 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 27, 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. 24, the eccentric amounts of the two eccentric portions 11 are equal to e, as shown in fig. 25, the fitting eccentric amount between the crankshaft 10 and the cylinder liner 20 is e (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, since the cross groove structure 30 is disposed coaxially with the cylinder liner 20), and the flange 50 includes an upper flange 52 and a lower flange 53, as shown in fig. 26, 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.
Optionally, a second rotation gap is provided between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder liner 20, and the size of the second rotation gap is 0.005 mm-0.1 mm.
As shown in fig. 1 to 5, 7, and 20 to 24, 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. 1 to 5, 7, and 20 to 24, 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 4, 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. 1 to 5, 7, and 20 to 24, the eccentric portion 11 is cylindrical.
Alternatively, the proximal end of the eccentric 11 is flush with the outer circumference of the shaft body portion 12 of the crankshaft 10.
Alternatively, the proximal end of the eccentric portion 11 protrudes from the outer circumference of the shaft body portion 12 of the crankshaft 10.
Alternatively, the proximal end of the eccentric portion 11 is located inside the outer circumference of the shaft body portion 12 of the crankshaft 10.
It should be noted that, in an embodiment of the present application, the slider 40 includes a plurality of sub-structures, and the plurality of sub-structures are spliced to form the through hole 41.
As shown in fig. 1 to 5, 7, and 20 to 24, the 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, the cross groove structure 30 has a center hole 32, and 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. 27, 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 arranged first sliding surfaces in sliding contact with the slide 40, the slide 40 has a second sliding surface cooperating with the first sliding surfaces, the slide 40 has a pressing surface 42 facing the end of the limiting channel 31, the pressing surface 42 acts as the head of the slide 40, the two second sliding surfaces are connected by the pressing surface 42, and the pressing surface 42 faces the variable volume chamber. 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 center of the arc surface and the center of the through hole 41 Equal to the eccentric amount of the eccentric portion 11. In FIG. 27, 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. 27 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 this 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 a variable volume cavity, the pump body assembly 83 has 4 variable volume cavities in total, during the rotation of the crankshaft 10, the crankshaft 10 rotates 2 circles, and a single variable volume cavity 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.
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.
Aiming at the problems of reducing the processing difficulty of parts and reducing the clearance volume and noise, the application respectively arranges two exhaust passages 51 on two flanges 50, so that the exhaust passages 51 are improved into a planar exhaust structure compared with the existing exhaust on the side wall of the cylinder sleeve 20, and the application is as follows:
as shown in fig. 1 to 27, the fluid machine includes two flanges 50, the two flanges 50 are respectively disposed at two axial ends of the cylinder liner 20, exhaust passages 51 are respectively formed on the two flanges 50, and the two exhaust passages 51 are respectively communicated with the variable volume chambers at the corresponding sides; wherein the cross-sectional area of the passage section of the exhaust passage 51 is 0.5% -35% of the projected area of the slider 40 in the sliding direction thereof.
The two flanges 50 are provided with the exhaust channels 51, and the two exhaust channels 51 are respectively communicated with the variable volume chambers on the corresponding sides, so that compared with the existing exhaust channels 51 which are arranged on the cambered surfaces of the side walls of the cylinder sleeve 20, the exhaust channels 51 are arranged on the planes of the flanges 50, the exhaust channels are beneficial to reducing noise influence caused by the existence of edges of the exhaust channels 51, uneven assembly of the cylinder sleeve 20 and the flanges 50 in the assembly process, and the like, and the exhaust path of the compressor is changed to avoid noise; in addition, since the exhaust passage 51 is formed on the plane of the flange 50 and belongs to the outer plane, compared with the arc surface formed on the side wall of the cylinder sleeve 20, the processing difficulty of the exhaust passage 51 is greatly reduced, the processing of parts is relatively easier, and the polishing of flanging or burrs and the like caused by processing is facilitated.
Further, since both ends in the length direction of the exhaust passage 51 of the compressor provided by the application are planar, the volume of the planar exhaust passage 51 is smaller, the clearance volume is smaller, and the refrigeration capacity and the power consumption are guaranteed.
Furthermore, by reasonably optimizing the cross-sectional area of the passage section of the exhaust passage 51 and the ratio of the projected area of the slider 40 in the sliding direction thereof, exhaust loss is avoided.
It should be noted that, in the present application, the gas compressed by the upper compression chamber is discharged through the upper flange 52, the gas compressed by the lower compression chamber is discharged through the lower flange 53, and the upper compression chamber, the lower compression chamber and the two exhaust passages 51 are independent from each other, which is beneficial to preventing the gas of the two compression chambers from affecting each other and generating noise such as pulsation caused by the exhaust of the cylinder liner 20.
It should be noted that, the existing exhaust on the cylinder liner 20 side belongs to indirect exhaust, that is, after the gas is exhausted, the gas firstly passes through the exhaust port of the cylinder liner 20 and then enters the exhaust cavity of the cylinder liner 20, then flows to the flange 50 from the suction communication cavity on the cylinder liner 20, and finally is exhausted from the flange 50, noise is easily generated when the whole exhaust period passes through the edge angle or the uneven edge part left when all parts are assembled, the exhaust through the two exhaust channels 51 on the two flanges 50 belongs to direct exhaust, the gas is directly exhausted into the shell, the exhaust path is shorter, and turbulent airflow is not easily generated.
In addition, in the existing no-cover-plate cylinder liner exhaust mode, compressed gas is exhausted from a side exhaust port of the cylinder liner and directly rushes to the wall surface of the shell, so that impact is caused to the wall surface of the shell, vibration and noise are generated, and the exhaust through the two exhaust channels 51 on the two flanges 50 provided by the application belongs to direct exhaust, so that the defect of exhaust at the side of the cylinder liner even on the wall surface can be reduced, and the harm of vibration noise is greatly reduced.
As shown in fig. 5, the projection of the slider 40 in the sliding direction thereof is semicircular.
As shown in fig. 16 and 17, the two exhaust passages 51 are schematically structured at angular positions in the circumferential direction of the upper flange 52 and the lower flange 53, respectively, and 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.
Specifically, as shown in fig. 16, the exhaust passage 51 of the assembled upper flange 52 is positioned in the circumferential direction of the upper flange 52 at an angle of 0 ° base line from the start of suction of the upper slide 40, the clockwise rotation angle is positive, and the arrangement position of the exhaust passage 51 in the circumferential direction of the upper flange 52 is in the angular range of (90 ° -arccos (C/D) to 90 ° + arccos (C/D)), where C is the distance between two relatively parallel straight line segments of the projection of the slide 40 in the axial direction of the through hole 41, and D is the inner diameter of the cylinder liner 20.
Further, as shown in fig. 17, the position of the exhaust passage 51 of the assembled lower flange 53 in the circumferential direction of the lower flange 53 is set to be in the angular range of (90 ° -arccos (C/D) to 90 ° + arccos (C/D)) with the angle at which the lower slider 40 starts to suck air being 0 ° base line, the clockwise rotation angle being positive, and the setting position of the exhaust passage 51 in the circumferential direction of the lower flange 53 is set to be in the angular range of (90 ° -arccos (C/D)) where C is the distance between two relatively parallel straight line segments of the projection of the slider 40 in the axial direction of the through hole 41, and D is the inner diameter of the cylinder liner 20.
As shown in fig. 16 to 19, the inner circumferential edges of both axial ends of the cylinder liner 20 are provided with oblique cutouts 27, and the two oblique cutouts 27 are respectively for communication with the two exhaust passages 51. In this way, the provision of the diagonal cuts 27 is advantageous in increasing the flow path of the gas, thereby reducing the loss of exhaust gas.
As shown in fig. 16 to 19, two exhaust passages 51 are provided concentrically in the axial direction of the cylinder liner 20, and the two diagonal cuts 27 are aligned in position in the circumferential direction of the cylinder liner 20.
Of course, in an embodiment of the present application, not shown, the two exhaust passages 51 are not disposed concentrically in the axial direction of the cylinder liner 20, and the two diagonal cuts 27 are not located uniformly in the circumferential direction of the cylinder liner 20.
In the present application, the sum of the projected area of the diagonal slit 27 on the inner circle of the cylinder liner 20 and the projected area of the diagonal slit 27 on the end surface of the cylinder liner 20 is equal to or larger than the cross-sectional area of the passage cross section of the exhaust passage 51. In this way, it is advantageous to increase the flow path of the gas, thereby reducing the exhaust loss.
In the present application, in order to reduce over-compression and power consumption, the end surface of the flange 50 facing the cylinder liner 20 is provided with a drainage groove 58, the drainage groove 58 is communicated with the exhaust passage 51, and the drainage groove 58 is arranged opposite to and communicated with the oblique cut 27. In this way, the over-compression and the power consumption are reduced, and the resonant cavity is also realized.
Specifically, as shown in fig. 8, the upper flange 52 is not provided with a drainage groove 58; fig. 9 to 11 show a schematic structure in which a drainage groove 58 is provided on the end surface of the upper flange 52 facing the cylinder liner 20.
Specifically, as shown in fig. 12, the lower flange 53 is not provided with a drainage groove 58; fig. 13 to 14 show a schematic structure in which a drainage groove 58 is formed in the end face of the upper flange 52 facing the cylinder liner 20.
In the present application, the cylinder liner 20 has at least one radial suction hole 21, the radial suction hole 21 is used for communicating with the variable volume chamber, the inner wall surface of the cylinder liner 20 has a suction chamber 23, and the radial suction hole 21 communicates with the variable volume chamber through the suction chamber 23. In this way, it is ensured that the suction chamber 23 can store a large amount of gas so that the variable volume chamber can be filled with suction gas, thereby enabling the suction gas to be sufficient, and when the suction gas is insufficient, the stored gas can be timely supplied to the variable volume chamber so as to ensure the compression efficiency of the compressor. In addition, the suction of the compressor is sufficient, and the performance and the refrigerating capacity of the compressor can be improved. The problem that various structures interfere with each other in design due to the compact structure of the pump body assembly 83 can be solved, so that the design is easier.
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.
Example 1
As shown in fig. 20, the number of the air suction cavities 23 is two, the two air suction cavities 23 are arranged at intervals along the axial direction of the cylinder sleeve 20, the cylinder sleeve 20 is also provided with an air suction communication cavity 24, the two air suction cavities 23 are communicated with the air suction communication cavity 24, and when the cylinder sleeve 20 is provided with one radial air suction hole 21, the radial air suction hole 21 is communicated with the two air suction cavities 23 through the air suction communication cavity 24. In this way, it is advantageous to increase the volume of the suction chamber 23, thereby reducing suction pressure pulsation.
Further, the air suction communication cavity 24 extends along the axial direction of the cylinder sleeve 20 for a second preset distance, and at least one end of the air suction communication cavity 24 penetrates through the axial end face of the cylinder sleeve 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.
Example two
As shown in fig. 21, two air suction chambers 23 are arranged at intervals along the axial direction of the cylinder sleeve 20, two radial air suction holes 21 are arranged, the two radial air suction holes 21 are in one-to-one correspondence with the two air suction chambers 23, and the two radial air suction holes 21 are respectively communicated with the corresponding volume chambers through the two air suction chambers 23.
Example III
As shown in fig. 22, one of the two flanges 50 has an intake passage 54, and the intake passage 54 and the exhaust passage 51 on the same flange 50 have a phase difference in the circumferential direction of the flange 50, the cylinder liner 20 has one radial suction hole 21, and the intake passage 54 and the radial suction hole 21 communicate with the two variable volume chambers, respectively.
Example IV
As shown in fig. 23, both the flanges 50 have intake passages 54, and the intake passages 54 and the exhaust passages 51 on the same flange 50 have a phase difference in the circumferential direction of the flange 50, and the two intake passages 54 communicate with the two variable volume chambers, respectively.
In the present application, as shown in fig. 3, both flanges 50 are connected to the cylinder liner 20 by fasteners 90.
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 invention 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 (16)
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) 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) is provided with two 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, the variable volume cavity is positioned in the sliding direction of the sliding block (40), and the crankshaft (10) rotates to drive the sliding block (40) to reciprocally slide in the limiting channels (31) and interact with the cross groove structure (30), so that the cross groove structure (30) and the sliding block (40) rotate in the cylinder sleeve (20);
The two flanges (50) are respectively arranged at the two axial ends of the cylinder sleeve (20), exhaust channels (51) are respectively formed in the two flanges (50), and the two exhaust channels (51) are respectively communicated with the variable-volume cavities at the corresponding sides;
wherein the cross-sectional area of the passage section of the exhaust passage (51) is 0.5% -35% of the projected area of the slider (40) in the sliding direction thereof.
2. The fluid machine according to claim 1, characterized in that the projection of the slider (40) in its sliding direction is semicircular.
3. A fluid machine as claimed in claim 1, wherein,
the projection of the sliding block (40) in the axial direction of the through hole (41) is provided with two relatively parallel straight line sections and an arc line section connecting the end parts of the two straight line sections;
the arrangement position of the exhaust passage (51) in the circumferential direction of the flange (50) is within an angle range of (90 ° -arccos (C/D) to 90 ° + arccos (C/D)), wherein C is a distance between two relatively parallel straight line segments of the projection of the slider (40) in the axial direction of the through hole (41), and D is an inner diameter of the cylinder liner (20).
4. Fluid machine according to claim 1, characterized in that the edges of the inner circles at the axial ends of the cylinder liner (20) are provided with oblique cuts (27), both of which oblique cuts (27) are respectively intended to communicate with both of the exhaust channels (51).
5. The fluid machine according to claim 4, wherein the fluid machine is further configured to,
the two exhaust passages (51) are concentrically arranged in the axial direction of the cylinder sleeve (20), and the positions of the two oblique notches (27) in the circumferential direction of the cylinder sleeve (20) are consistent; or alternatively, the first and second heat exchangers may be,
the two exhaust passages (51) are arranged non-concentrically in the axial direction of the cylinder liner (20), and the positions of the two diagonal cuts (27) in the circumferential direction of the cylinder liner (20) are non-uniform.
6. The fluid machine according to claim 4, wherein a sum of a projected area of the diagonal slit (27) on an inner circumference of the cylinder liner (20) and a projected area of the diagonal slit (27) on an end surface of the cylinder liner (20) is equal to or larger than a cross-sectional area of a passage cross-section of the exhaust passage (51).
7. The fluid machine according to claim 4, wherein a drainage groove (58) is formed in an end face of the flange (50) facing the cylinder sleeve (20), the drainage groove (58) is communicated with the exhaust channel (51), and the drainage groove (58) is opposite to and communicated with the oblique notch (27).
8. The fluid machine according to claim 1, characterized in that the cylinder liner (20) has at least one radial suction hole (21), the radial suction hole (21) being adapted to communicate with the variable volume chamber, the inner wall surface of the cylinder liner (20) having a suction chamber (23), the radial suction hole (21) being adapted to communicate with the variable volume chamber through the suction chamber (23).
9. The fluid machine according to claim 8, wherein the suction chamber (23) extends a first predetermined distance around the circumference of the inner wall surface of the cylinder liner (20) to form an arc-shaped suction chamber (23).
10. The fluid machine according to claim 8, wherein the number of the suction cavities (23) is two, the two suction cavities (23) are arranged at intervals along the axial direction of the cylinder sleeve (20), the cylinder sleeve (20) is further provided with a suction communication cavity (24), the two suction cavities (23) are communicated with the suction communication cavity (24), and when the cylinder sleeve (20) is provided with one radial suction hole (21), the radial suction hole (21) is communicated with the two suction cavities (23) through the suction communication cavity (24).
11. The fluid machine according to claim 10, wherein the suction communication chamber (24) extends a second predetermined distance in the axial direction of the cylinder liner (20), at least one end of the suction communication chamber (24) penetrating through an axial end face of the cylinder liner (20).
12. The fluid machine according to claim 8, wherein the number of the air suction cavities (23) is two, the two air suction cavities (23) are arranged at intervals along the axial direction of the cylinder sleeve (20), the number of the radial air suction holes (21) is two, the two radial air suction holes (21) are in one-to-one correspondence with the two air suction cavities (23), and the two radial air suction holes (21) are respectively communicated with the corresponding variable volume cavities through the two air suction cavities (23).
13. The fluid machine according to claim 8, wherein one of the two flanges (50) has an intake passage (54), and the intake passage (54) and the exhaust passage (51) on the same flange (50) have a phase difference in the circumferential direction of the flange (50), and the cylinder liner (20) has one radial suction hole (21), and the intake passage (54) and the radial suction hole (21) are respectively communicated with the two variable volume chambers.
14. The fluid machine according to claim 8, wherein both the flanges (50) have intake passages (54), and the intake passages (54) and the exhaust passages (51) on the same flange (50) have a phase difference in the circumferential direction of the flange (50), and both the intake passages (54) are respectively communicated with both the variable volume chambers.
15. The fluid machine according to any one of claims 1 to 14, 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.
16. 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 15.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210563914.3A CN117145766A (en) | 2022-05-23 | 2022-05-23 | Fluid machine and heat exchange device |
| PCT/CN2022/140955 WO2023226409A1 (en) | 2022-05-23 | 2022-12-22 | Fluid machine and heat exchange device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210563914.3A CN117145766A (en) | 2022-05-23 | 2022-05-23 | Fluid machine and heat exchange device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117145766A true CN117145766A (en) | 2023-12-01 |
Family
ID=88899333
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210563914.3A Pending CN117145766A (en) | 2022-05-23 | 2022-05-23 | Fluid machine and heat exchange device |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN117145766A (en) |
| WO (1) | WO2023226409A1 (en) |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59155580A (en) * | 1983-02-25 | 1984-09-04 | Hitachi Ltd | Capacity control type compressor |
| CN105987004B (en) * | 2015-01-28 | 2018-02-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Sliding-vane compressor and its exhaust structure |
| CN106438359B (en) * | 2015-08-07 | 2019-01-08 | 珠海格力电器股份有限公司 | Compressor, heat exchange device and operation method of compressor |
| CN111963435B (en) * | 2020-07-24 | 2022-08-05 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN113638883A (en) * | 2021-09-23 | 2021-11-12 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body subassembly, compressor and air conditioner |
-
2022
- 2022-05-23 CN CN202210563914.3A patent/CN117145766A/en active Pending
- 2022-12-22 WO PCT/CN2022/140955 patent/WO2023226409A1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| WO2023226409A1 (en) | 2023-11-30 |
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