CN117145766B - Fluid machinery and heat exchange equipment - Google Patents
Fluid machinery and heat exchange equipmentInfo
- Publication number
- CN117145766B CN117145766B CN202210563914.3A CN202210563914A CN117145766B CN 117145766 B CN117145766 B CN 117145766B CN 202210563914 A CN202210563914 A CN 202210563914A CN 117145766 B CN117145766 B CN 117145766B
- Authority
- CN
- China
- Prior art keywords
- crankshaft
- fluid machine
- suction
- exhaust
- cylinder sleeve
- 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.)
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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
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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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
- 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 provided with two eccentric parts along the axial direction of the crankshaft, the crankshaft and the cylinder sleeve are eccentrically arranged, the eccentric distance is fixed, the cross groove structure is rotatably arranged in the cylinder sleeve, two limiting channels of the cross groove structure are sequentially arranged along the axial direction of the crankshaft, 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 mode and form a variable volume cavity, the variable volume cavity is positioned in the sliding direction of the sliding block, the two flanges are respectively provided with an exhaust channel, the two exhaust channels are respectively communicated with the variable volume cavity on the corresponding side, and the sectional area of the channel section of each exhaust channel is 0.5% -35% of the projection area of the sliding block in the sliding direction. 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, wherein the crankshaft is provided with two eccentric portions along an axial direction thereof, the crankshaft is eccentrically disposed with respect to the cylinder liner with a fixed eccentric distance, the cross groove structure is rotatably disposed in the cylinder liner, the cross groove structure has two limiting passages sequentially disposed along an axial direction of the crankshaft, an extending direction of the limiting passages is perpendicular to the axial direction of the crankshaft, the slider has a through hole, the slider is provided with two eccentric portions, the two eccentric portions extend into the two through holes of the two sliders, the two sliders are slidably disposed in the two limiting passages, respectively, and form a variable volume chamber in a sliding direction of the slider, the crankshaft rotates to drive the slider to reciprocally slide in the limiting passages while interacting with the cross groove structure, so that the cross groove structure and the slider rotate in the cylinder liner, the two flanges are disposed at both axial ends of the cylinder liner, respectively, and the two flanges are provided with exhaust passages communicating with respective variable volume chambers on respective sides, wherein a cross section of the exhaust passages is 0.5% -35% of a projected area of a cross section of the slider in a 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 ends of the two straight line sections, the arrangement position of the exhaust channel in the circumferential direction of the flange is in the angle range of (90-arccos (C/D) -90 degrees+ arccos (C/D)), wherein C is the distance between the two relatively parallel straight line sections of the projection of the sliding block in the axial direction of the through hole, and D is the inner circle diameter of the cylinder sleeve.
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 arranged concentrically 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 non-concentrically in the axial direction of the cylinder sleeve, and the two oblique cuts are inconsistent in position in the circumferential direction of the cylinder sleeve.
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 of the invention, the exhaust channels are arranged on the two flanges, and the two exhaust channels are respectively communicated with the variable volume chambers on the corresponding sides, so that the exhaust channels are arranged on the planes of the flanges, compared with the existing exhaust channels arranged on the cambered surfaces of the side walls of the cylinder sleeve, the exhaust channels are beneficial to reducing noise influence caused by the existence of edges and corners of the exhaust channels and uneven assembly of the cylinder sleeve and the flange in the assembly process, and noise is avoided by changing the exhaust path of the fluid machinery.
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 invention;
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, an eccentric part, 12, a shaft body part;
20. cylinder sleeve; 21, radial suction holes, 23, suction cavities, 24, suction communication cavities, 27 and oblique cuts;
30. The cross groove structure, 31, limiting channels, 32, central holes;
40. A slider 41, a through hole 42 and a pressing surface;
50. The flange, 51, the exhaust channel, 52, the upper flange, 53, the lower flange, 54, the air inlet channel, 58, the drainage groove;
80. The liquid distributor comprises a liquid distributor component, 81, a shell component, 82, a motor component, 83, a pump body component, 84, an upper cover component and 85, a lower cover component;
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 principle of a compressor operation mechanism is proposed based on a cross slide mechanism, that is, a point O 1 is taken as a cylinder center, a point O 2 is taken as a driving shaft center, a point O 3 is taken as a slide center, the cylinder and the driving shaft are eccentrically arranged, and the slide center O 3 performs circular motion on a circle with a diameter of O 1O2.
In the principle of the running mechanism, the cylinder center O 1 and the driving shaft center O 2 are used as two rotation centers of the running mechanism, and meanwhile, the midpoint O 0 of the line segment O 1O2 is used as a virtual center of the slide block center O 3, so that the slide block reciprocates relative to the cylinder and also reciprocates relative to the driving shaft.
Since the midpoint O 0 of the line segment O 1O2 is a virtual center, a balance system cannot be set, and thus the high-frequency vibration characteristic of the compressor is deteriorated, on the basis of the principle of the above-described operation mechanism, as shown in fig. 31, a motion mechanism using O 0 as a center of a driving shaft, that is, a cylinder center O 1 and a driving shaft center O 0 as two rotation centers of the motion mechanism, the driving shaft having an eccentric portion, a slider coaxially disposed with the eccentric portion, and an assembly eccentric amount of the driving shaft and the cylinder being equal to an eccentric amount of the eccentric portion, is proposed, so that the slider center O 3 performs a circular motion with the driving shaft center O 0 as a center and with O 1O0 as a radius.
The corresponding one set of running mechanism comprises a cylinder, a limit groove structure, a sliding block and a driving shaft, wherein the limit groove structure is rotatably arranged in the cylinder, the cylinder and the limit groove structure are coaxially arranged, namely, the center O 1 of the cylinder is also the center of the limit groove structure, the sliding block reciprocates relative to the limit groove structure, the sliding block is coaxially assembled with the eccentric part of the driving shaft, the sliding block performs circular motion around the shaft body part of the driving shaft, and particularly, the moving process is that 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 simultaneously rotates relative to the eccentric part, and the sliding block reciprocates in the limit groove of the limit groove structure and pushes the limit groove structure to rotate.
However, as shown in fig. 32, the length of the arm L of force for driving the slider to rotate is l=2e×cos θ×cos θ, where e is the eccentric amount of the eccentric portion, and θ is the angle between the O 1O0 connecting line and the sliding direction of the slider in the limiting groove.
As shown in fig. 33, when the cylinder center O 1 (i.e., the center of the limit groove structure) and the center of the eccentric portion overlap, the resultant force of the driving shaft passes through the center of the limit groove structure, i.e., the torque applied to the limit groove structure is zero, the limit groove structure cannot be rotated, and the moving mechanism at this time is at the dead point position, and cannot drive the slider 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 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, the eccentric amounts of the two eccentric parts 11 are equal, the crankshaft 10 and the cylinder sleeve 20 are eccentrically arranged, 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, a phase difference of a second included angle B is formed between the extending directions of the two limiting channels 31, the first included angle A is twice as large as the second included angle B, 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 correspondingly slide in the two limiting channels 31 and form a variable volume cavity, the variable volume cavity is positioned in the sliding direction of the sliding block 40, the sliding block 10 rotates to drive the sliding block 40 to slide in the limiting channels 31 and simultaneously reciprocate in the limiting channels 31 and the cross groove structure 30 to enable the sliding block 40 to rotate in the cross groove structure 30.
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 is operated, the crankshaft 10 rotates around the axis O 0 of the crankshaft 10, the cross groove structure 30 revolves around the axis O 0 of the crankshaft 10, the axis O 0 of the crankshaft 10 and the axis O 1 of the cross groove structure 30 are eccentrically arranged and have a fixed eccentric distance, the first slide block 40 moves circumferentially around the axis O 0 of the crankshaft 10, the distance between the center O 3 of the first slide block 40 and the axis O 0 of the crankshaft 10 is equal to the eccentric amount of the first eccentric part 11 corresponding to the crankshaft 10, the eccentric amount is equal to the eccentric distance between the axis O 0 of the crankshaft 10 and the axis O 1 of the cross groove structure 30, the crankshaft 10 rotates to drive the first slide block 40 to do circumferential movement, the first slide 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 moves circumferentially around the axis O 0 of the axis O10 as the center of the crankshaft 10, the distance between the center O 4 of the second slide block 40 and the axis O 0 of the crankshaft 10 is equal to the eccentric distance between the second slide block 10 and the cross groove structure and the eccentric channel of the second eccentric structure 1.
The fluid machine operating in the above-described manner constitutes a slider-cross mechanism, which adopts the slider-cross mechanism principle in which the two eccentric portions 11 of the crankshaft 10 serve as the first link L 1 and the second link L 2, respectively, the two limiting passages 31 of the cross groove structure 30 serve as the third link L 3 and the fourth link L 4, respectively, and the lengths of the first link L 1 and the second link L 2 are equal (refer to fig. 28).
As shown in fig. 28, a first included angle a is formed between the first link L 1 and the second link L 2, and a second included angle B is formed between the third link L 3 and the fourth link L 4, wherein the first included angle a is twice the second included angle B.
As shown in fig. 29, a connection line between an axis O 0 of the crankshaft 10 and an axis O 1 of the intersecting groove structure 30 is a connection line O 0 O1, a third included angle C is formed between the first connecting rod L 1 and the connection line O 0 O1, a fourth included angle D is formed between the corresponding third connecting rod L 3 and the connection line O 0 O1, wherein the third included angle C is twice the fourth included angle D, a fifth included angle E is formed between the second connecting rod L 2 and the connection line O 0 O1, a sixth included angle F is formed between the corresponding fourth connecting rod L 4 and the connection line O 0 O1, wherein the fifth included angle E is twice the sixth included angle F, the sum of the third included angle C and the fifth included angle E is the first included angle a, and the sum of the fourth included angle D and the sixth included angle F is the second included angle B.
Further, the operation method further comprises the steps that the rotation angular speed of the sliding block 40 relative to the eccentric part 11 is the same as the revolution angular speed of the sliding block 40 around the axis O 0 of the crankshaft 10, and the revolution angular speed of the crossed groove structure 30 around the axis O 0 of the crankshaft 10 is the same as the rotation angular speed of the sliding block 40 relative to the eccentric part 11.
Specifically, the axis O 0 of the crankshaft 10 corresponds to the rotation centers of the first link L 1 and the second link L 2, and the axis O 1 of the intersecting groove structure 30 corresponds to the rotation centers of the third link L 3 and the fourth link L 4; the two eccentric parts 11 of the crankshaft 10 are respectively used as a first connecting rod L 1 and a second connecting rod L 2, the two limiting channels 31 of the cross groove structure 30 are respectively used as a third connecting rod L 3 and a fourth connecting rod L 4, and the lengths of the first connecting rod L 1 and the second connecting rod L 2 are equal, so that when the crankshaft 10 rotates, the eccentric parts 11 on the crankshaft 10 drive the corresponding slide blocks 40 to revolve around the axis O 0 of the crankshaft 10, and simultaneously the slide blocks 40 can rotate relative to the eccentric parts 11, and the relative rotation speeds of the two slide blocks are the same, as the first slide block 40 and the second slide block 40 respectively reciprocate in the two corresponding limiting channels 31 and drive the cross groove structure 30 to do circular motion, the motion direction of the two slide blocks 40 always has the phase difference of the second included angle B, when one of the two slide blocks 40 is at the dead point position, the eccentric parts 11 for driving the other slide blocks 40 have the maximum driving torque, and the eccentric parts 11 with the maximum driving torque can rotate relative to the eccentric parts 11, so that the slide blocks 40 can rotate relative to the eccentric parts, and the two slide blocks 40 can rotate relative to the corresponding slide blocks, thereby drive the two slide blocks 40 to rotate to keep the cross groove structure 30 to keep away from the normal dead point position, thereby realizing the mechanical motion of the fluid, and the mechanical motion of the fluid is realized, and the stable motion of the fluid motion is realized by the mechanical motion, and the stable the movement, and the fluid motion position of the position through the mechanical motion, and the position of the position through the dead center, and the movement through the mechanical motion and the dead center, and the position and the mechanical rotation position and the stable through the dead and the dead center, thereby ensuring the operational reliability of the heat exchange device.
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 uses the axis O 0 of the crankshaft 10 as the center and uses the connecting line O 0O1 as the 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 formed between the crankshaft 10 and the flange 50, and the first assembly gap ranges from 0.005mm to 0.05mm.
Preferably, the first assembly gap ranges from 0.01 mm to 0.03mm.
Optionally, two sliders 40 are respectively concentric with the two eccentric portions 11, the sliders 40 do circular motion around the axis of the crankshaft 10, a first rotation gap is formed between the hole 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 formed between the outer peripheral surface of the cross groove structure 30 and the inner wall surface of the cylinder sleeve 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.
In the application, the first included angle A is 160-200 degrees, and 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 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. 27, the center of the through hole 41 of the slider 40 is O Sliding block , and the distances between the centers of the two arc 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 where the centers of the two arc 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.
Optionally, the radius of curvature of the cambered surface has a difference value with the radius of the inner circle of the cylinder sleeve 20, and the difference value ranges from-0.05 mm to 0.025mm.
Preferably, the difference is in the range of-0.02 to 0.02mm.
In the present application, the projected area S Sliding block of the pressing surface 42 in the sliding direction of the slider 40 and the area S Row of rows of the compression exhaust port 22 of the cylinder liner 20 satisfy the value S Sliding block /S Row of rows of 8 to 25.
Preferably, the value of S Sliding block /S Row of rows is 12-18.
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 component 80, a housing component 81, a motor component 82, a pump component 83, an upper cover component 84 and a lower cover component 85, where the dispenser component 80 is disposed outside the housing component 81, the upper cover component 84 is assembled at the upper end of the housing component 81, the lower cover component 85 is assembled at the lower end of the housing component 81, the motor component 82 and the pump component 83 are both located inside the housing component 81, and the motor component 82 is located above the pump component 83, or the motor component 82 is located below the pump component 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 assembly process of the whole pump body assembly 83 is as follows, the lower flange 53 is fixed on the cylinder sleeve 20, the two sliding blocks 40 are respectively arranged in the two corresponding limiting channels 31, the two eccentric parts 11 of the crankshaft 10 respectively extend into the two through holes 41 of the two corresponding sliding blocks 40, the assembled crankshaft 10, the crossed groove structure 30 and the two sliding blocks 40 are arranged in the cylinder sleeve 20, one end of the crankshaft 10 is arranged on the lower flange 53, and the other end of the crankshaft 10 passes through the upper flange 52 to be arranged, and particularly, refer to 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, the two exhaust passages 51 are respectively communicated with the variable volume chambers at the corresponding sides, wherein the sectional area of the passage section of the exhaust passage 51 is 0.5% -35% of the projected area of the sliding block 40 in the sliding direction.
The two flanges 50 are respectively provided with the exhaust channels 51, and the two exhaust channels 51 are respectively communicated with the variable-volume cavities on the corresponding sides, so that the exhaust channels 51 are arranged on the planes of the flanges 50, compared with the existing exhaust channels which are arranged on the cambered surfaces of the side walls of the cylinder sleeve 20, noise influence caused by the existence of edges and corners of the exhaust channels 51 and uneven assembly of the cylinder sleeve 20 and the flanges 50 in the assembly process is reduced, noise is avoided by changing the exhaust path of the compressor, and in addition, the exhaust channels 51 are arranged on the planes of the flanges 50 and belong to the outer planes, compared with the exhaust channels which are arranged on the cambered surfaces of the side walls of the cylinder sleeve 20, processing difficulty of the exhaust channels 51 is greatly reduced, processing of parts is relatively easier, and flanging or burrs and the like caused by processing are 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 exhaust passage 51 is positioned in the circumferential direction of the upper flange 52 at an angle ranging from (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 in such a manner that the suction angle of the lower slider 40 is set to be 0 ° baseline, the clockwise rotation angle is set to be positive, and the setting position of the exhaust passage 51 in the circumferential direction of the lower flange 53 is set in the angular range of (90 ° -arccos (C/D) -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, and as shown in fig. 9 to 11, the upper flange 52 is provided with a drainage groove 58 on the end face facing the cylinder liner 20.
Specifically, as shown in fig. 12, the lower flange 53 is not provided with a drainage groove 58, and as shown in fig. 13 to 14, the upper flange 52 is provided with a drainage groove 58 on the end face 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 refer to 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," "upper" and "upper surface," "above" and the like, may be used herein for ease of description to describe one device or feature's spatial relationship 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 process is carried out, the exemplary term "above" may be included. Upper and lower. Two orientations 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 invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
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) 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;
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) -90 ° + arccos (C/D)), wherein 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 sleeve (20).
2. The fluid machine according to claim 1, characterized in that the projection of the slider (40) in its sliding direction is semicircular.
3. 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).
4. A fluid machine according to claim 3, wherein,
The two exhaust passages (51) are concentrically arranged in the axial direction of the cylinder sleeve (20), the two oblique cuts (27) are positioned in agreement with each other in the circumferential direction of the cylinder sleeve (20), or,
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.
5. A fluid machine according to claim 3, wherein the sum of the projected area of the oblique slit (27) on the inner circumference of the cylinder liner (20) and the projected area of the oblique 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).
6. A fluid machine according to claim 3, wherein the flange (50) is provided with a drainage groove (58) on the end face facing the cylinder sleeve (20), the drainage groove (58) is communicated with the exhaust passage (51), and the drainage groove (58) is opposite to and communicated with the oblique notch (27).
7. 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).
8. The fluid machine according to claim 7, 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).
9. The fluid machine according to claim 7, 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).
10. The fluid machine according to claim 9, 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).
11. The fluid machine according to claim 7, 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).
12. The fluid machine according to claim 7, 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.
13. The fluid machine according to claim 7, 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.
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 (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210563914.3A CN117145766B (en) | 2022-05-23 | 2022-05-23 | Fluid machinery and heat exchange equipment |
| 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 CN117145766B (en) | 2022-05-23 | 2022-05-23 | Fluid machinery and heat exchange equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN117145766A CN117145766A (en) | 2023-12-01 |
| CN117145766B true CN117145766B (en) | 2025-12-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210563914.3A Active CN117145766B (en) | 2022-05-23 | 2022-05-23 | Fluid machinery and heat exchange equipment |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN117145766B (en) |
| WO (1) | WO2023226409A1 (en) |
Citations (2)
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|---|---|---|---|---|
| JPS59155580A (en) * | 1983-02-25 | 1984-09-04 | Hitachi Ltd | Capacity control type compressor |
| CN111963435A (en) * | 2020-07-24 | 2020-11-20 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102828951B (en) * | 2011-06-13 | 2014-12-31 | 广东美芝制冷设备有限公司 | Double-slip-sheet type rotary 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 |
| CN106704183B (en) * | 2015-08-07 | 2019-03-29 | 珠海格力电器股份有限公司 | Fluid machine, heat exchange device and operation method of fluid machine |
| 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 |
| CN105485021B (en) * | 2016-01-25 | 2018-11-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Duplex cylinder compressor and air conditioner |
| CN206206157U (en) * | 2016-10-13 | 2017-05-31 | 广东美芝精密制造有限公司 | Rotary compressor and the compression mechanism for rotary compressor |
| CN106438375B (en) * | 2016-10-17 | 2018-05-18 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of compressor and its exhaust structure |
| 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 assemblies, compressors and air conditioners |
-
2022
- 2022-05-23 CN CN202210563914.3A patent/CN117145766B/en active Active
- 2022-12-22 WO PCT/CN2022/140955 patent/WO2023226409A1/en not_active Ceased
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59155580A (en) * | 1983-02-25 | 1984-09-04 | Hitachi Ltd | Capacity control type compressor |
| CN111963435A (en) * | 2020-07-24 | 2020-11-20 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2023226409A1 (en) | 2023-11-30 |
| CN117145766A (en) | 2023-12-01 |
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