CN117145773B - Fluid machinery and heat exchange equipment - Google Patents
Fluid machinery and heat exchange equipmentInfo
- Publication number
- CN117145773B CN117145773B CN202210568373.3A CN202210568373A CN117145773B CN 117145773 B CN117145773 B CN 117145773B CN 202210568373 A CN202210568373 A CN 202210568373A CN 117145773 B CN117145773 B CN 117145773B
- Authority
- CN
- China
- Prior art keywords
- exhaust
- crankshaft
- fluid machine
- cylinder sleeve
- axial direction
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The invention provides a fluid machine and heat exchange equipment, which comprises a crankshaft, a cylinder sleeve, a cross groove structure, sliding blocks and two flanges, wherein the crankshaft is provided with two eccentric parts, the crankshaft and the cylinder sleeve are eccentrically arranged and have fixed eccentric distances, 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 extending direction of the limiting channels is perpendicular to the axial direction of the crankshaft, the two eccentric parts correspondingly extend into two through holes of the two sliding blocks, at least one flange is provided with an exhaust channel, two exhaust ports are arranged on the side wall surface of the cylinder sleeve, the two exhaust ports are arranged at intervals along the axial direction of the cylinder sleeve and are communicated with the exhaust channels, the cross section area of the hole section of the exhaust port is S1, and the volume of a single variable volume cavity is V1/S1 is more than or equal to 3300. The invention solves the problems of low energy efficiency, high noise and low exhaust loss of the compressor in the prior art.
Description
Technical Field
The invention relates to the technical field of heat exchange systems, in particular to a fluid machine and heat exchange equipment.
Background
The fluid machinery in the prior art includes compressors, expanders, and the like. Taking a compressor as an example.
According to national energy-saving and environment-friendly policies and consumer requirements for air conditioning comfort, the air conditioning industry is always pursuing high efficiency and low noise. The compressor acts as the heart of the air conditioner, having a direct impact on the energy efficiency and noise level of the air conditioner. The rolling rotor type compressor is used as a main stream of household air conditioner compressors, has been developed for nearly one hundred years, is relatively mature, is limited by a structural principle, and has limited optimization space. Therefore, it is highly desirable to provide a compressor having the characteristics of high energy efficiency, low noise, and the like.
In addition, the existing partial compressors have poor efficiency due to a large loss of exhaust gas.
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 low exhaust loss 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 slot structure, a slider and two flanges, wherein the crankshaft is provided with two eccentric portions along an axial direction thereof, the crankshaft and the cylinder liner are eccentrically arranged and have a fixed eccentric distance, the cross slot structure is rotatably arranged in the cylinder liner, the cross slot structure is provided with two limiting channels, the two limiting channels are sequentially arranged along the axial direction of the crankshaft, an extending direction of the limiting channels is perpendicular to the axial direction of the crankshaft, the slider is provided with two through holes, the two eccentric portions correspondingly extend into the two through holes of the two sliders, the two sliders correspondingly slide in the two limiting channels and form a variable volume cavity, the variable volume cavity is located in a sliding direction of the slider, the crankshaft rotates to drive the slider to slide reciprocally in the limiting channels and simultaneously interact with the cross slot structure, so that the cross slot structure and the slider rotate in the cylinder liner, the two flanges are respectively arranged at two axial ends of the cylinder liner, at least one flange is provided with an exhaust channel, wherein the side wall surface of the cylinder liner is provided with two exhaust ports, the two exhaust ports are axially spaced along the axial direction of the cylinder liner, and the two exhaust ports are respectively arranged, and the two exhaust ports have a volume of a single cross section of S1 and a V1 is equal to or a 0, and a 2.
Further, the positions of the two exhaust ports in the circumferential direction of the cylinder liner are identical.
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 port in the circumferential direction of the cylinder sleeve is within the angle range of (arccos (2R/B) -2X arccos (2R/B)), wherein R is the inner circle radius of the cylinder sleeve, and B 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.
Further, an exhaust cavity is formed in the outer wall of the cylinder sleeve, the exhaust port is communicated to the exhaust cavity through the inner wall of the cylinder sleeve, the fluid machine further comprises an exhaust valve assembly, the exhaust valve assembly is arranged in the exhaust cavity and corresponds to the exhaust port, the exhaust valve assembly is in two groups, and the two groups of exhaust valve assemblies are respectively corresponding to the two exhaust ports.
Further, a communication hole is further formed in the axial end face of the cylinder sleeve, the communication hole is communicated with the exhaust cavity, and the communication hole is communicated with the exhaust channel.
Further, two exhaust cavities are arranged at intervals along the axial direction of the cylinder sleeve, and the two exhaust cavities are arranged in one-to-one correspondence with and communicated with the two exhaust ports.
Further, the two exhaust chambers are communicated through an exhaust communication hole extending in the axial direction of the cylinder liner.
Further, the distance between the plane where the end of the exhaust port, which is communicated with the exhaust cavity, is K and the axis of the cylinder sleeve, and the inner circle radius of the cylinder sleeve is R, wherein K-R is less than or equal to 1mm and less than or equal to 5mm.
Further, the cross section area of the exhaust cavity in the axial direction of the cylinder sleeve is S2, the height of the single exhaust cavity in the axial direction of the cylinder sleeve is M, and the displacement of the fluid machine is V, wherein 0.5-V-5 is smaller than or equal to 5.
Further, an exhaust cavity is formed in the outer wall of the cylinder sleeve, a boss structure is arranged on the cavity wall surface of the exhaust cavity, and the exhaust port penetrates through the boss structure from the inner wall of the cylinder sleeve and is communicated with the exhaust cavity.
Further, the thickness of the boss structure in the extending direction of the exhaust port is N, wherein N is less than or equal to 0.05mm and less than or equal to 3mm.
Further, the exhaust cavity penetrates through the outer wall surface of the cylinder sleeve, and the fluid machine further comprises an exhaust cover plate which is connected with the cylinder sleeve and seals the exhaust cavity.
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 exhaust channel is formed in at least one of the two flanges, meanwhile, two exhaust ports are formed in the side wall surface of the cylinder sleeve, the two exhaust ports are arranged at intervals along the axial direction of the cylinder sleeve and are communicated with the exhaust channel, in addition, the cross section area of the hole section of the exhaust port is S1, the volume of a single variable volume cavity is V1, wherein V1/S1 is less than or equal to 750 and less than or equal to 3300, so that the exhaust reliability of the fluid machine is ensured, the exhaust loss of the fluid machine is reduced, and the efficiency of the fluid machine is improved.
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 a first embodiment of the present invention;
FIG. 2 shows a schematic structural view of a pump body assembly of the compressor of FIG. 1;
FIG. 3 shows an exploded view of the pump body assembly of FIG. 2;
FIG. 4 shows a schematic 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 structural view of the shaft body portion and the eccentric amounts of the two eccentric portions of the crankshaft of FIG. 4;
FIG. 7 is a schematic cross-sectional structural view showing the amount of assembly eccentricity of the crankshaft and cylinder liner of FIG. 3;
FIG. 8 is a schematic view showing the structure of the eccentricity between the cylinder liner and the lower flange in FIG. 3;
FIG. 9 shows a schematic view of the slider of FIG. 3 in the axial direction of the through hole;
FIG. 10 is a schematic view showing a state structure of the compressor of FIG. 3 at the start of suction;
FIG. 11 is a schematic view showing a state structure of the compressor of FIG. 3 during suction;
FIG. 12 is a schematic view showing a state structure of the compressor of FIG. 3 at the end of suction;
FIG. 13 is a schematic view showing a state structure of the compressor of FIG. 3 when compressed gas is supplied;
FIG. 14 is a schematic view showing a state structure of the compressor of FIG. 3 in a discharge process;
FIG. 15 shows a schematic view of the compressor of FIG. 3 in a state at the end of discharge;
FIG. 16 shows a schematic structural view of the cylinder liner of FIG. 3;
FIG. 17 shows a schematic cross-sectional structural view of the cylinder liner of FIG. 3, showing the angular range of the exhaust ports disposed in the circumferential direction of the cylinder liner;
FIG. 18 shows a schematic cross-sectional structure of the cylinder liner of FIG. 3, showing K in relation to R;
FIG. 19 shows a schematic cross-sectional structural view of the pump body assembly of FIG. 2 from another perspective, showing an assembly eccentricity e between the crankshaft and cylinder liner;
FIG. 20 shows a schematic cross-sectional structural view of the cylinder liner of FIG. 2, with the cross-slot structure, the slide blocks, and the crankshaft omitted;
FIG. 21 shows a schematic view of the exhaust chamber side of the cylinder liner of FIG. 3;
FIG. 22 shows a schematic view of the exhaust chamber side of a cylinder liner with boss structures at the exhaust ports in accordance with an alternative embodiment of the present invention;
FIG. 23 shows a schematic view of the cylinder liner of FIG. 22 in partial cross-section;
FIG. 24 shows a schematic structural view of a cross section of the slider of FIG. 3 in its sliding direction;
Fig. 25 shows a schematic structural view of a pump body assembly according to a second embodiment of the present invention;
fig. 26 shows a schematic structural view of a pump body assembly according to a third embodiment of the present invention;
FIG. 27 shows a schematic structural view of a pump body assembly according to a fourth embodiment of the present invention;
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 is a schematic view showing the principle of the mechanism of operation of the compressor of FIG. 31, wherein the center of the limit slot structure coincides with the center of the eccentric portion;
FIG. 34 shows a graphical representation of compressor discharge loss, COP, clearance volume versus V1/S1.
Wherein the above figures include the following reference numerals:
10. a crankshaft, 11, an eccentric part, 12, a shaft body part;
20. The cylinder sleeve, the radial suction hole, the 22, the exhaust hole, the 23, the suction cavity, the 24, the suction communication cavity, the 25, the exhaust cavity, the 26, the communication hole, the 28, the exhaust communication hole, the 29 and the boss structure;
30. the cross groove structure, 31, limiting channels, 311, a variable volume cavity, 32, a central hole;
40. a slider 41, a through hole 42 and a pressing surface;
50. the device comprises a flange, an exhaust channel, a 52, an upper flange, a 53 and a lower flange;
70. an exhaust cover plate;
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, and a lower cover component.
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, the invention provides a fluid machine, a heat exchange device and an operation method of the fluid machine, wherein the heat exchange device comprises the fluid machine, and the fluid machine is operated by adopting the operation method.
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 311, the crankshaft 10 is positioned in the sliding direction of the sliding block 40, the two limiting channels 31 are sequentially arranged along the axial direction of the crankshaft 10, and the cross groove structure 30 is simultaneously rotated to drive the sliding block 40 and the cross groove structure 30 to rotate.
By arranging the cross groove structure 30 in a structure form with two limiting channels 31 and correspondingly arranging two sliding blocks 40, two eccentric parts 11 of a crankshaft correspondingly extend into two through holes 41 of the two sliding blocks 40, simultaneously, the two sliding blocks 40 correspondingly slide in the two limiting channels 31 and form a variable volume cavity 311, as a first included angle A between the two eccentric parts 11 is twice as large as a second included angle B between extending directions of the two limiting channels 31, when one of the two sliding blocks 40 is at a dead point position, namely, the driving torque of the eccentric part 11 corresponding to the sliding block 40 at the dead point position is 0, the sliding block 40 at the dead point position cannot continuously rotate, and at the moment, the driving torque of the other eccentric part 11 of the two eccentric parts 11 drives the corresponding sliding block 40 to be the maximum value, so that the corresponding sliding block 40 can be normally driven to rotate by the sliding block 40, the cross groove structure 30 is driven to rotate by the cross groove structure 30, the sliding block 40 at the dead point position is driven to continuously rotate by the cross groove structure 30, the reliability of the mechanical movement of the fluid is ensured, the mechanical movement is avoided, and the reliability of the mechanical movement is ensured, and the working reliability is ensured.
In addition, the fluid machinery provided by the application can stably run, namely, the energy efficiency of the compressor is ensured to be higher, the noise is lower, and therefore, the working reliability of the heat exchange equipment is ensured.
In the present application, the first angle a and the second angle B are not zero.
As shown in fig. 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. 29, 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.
In order to solve the problems of low energy efficiency and high noise of the compressor in the prior art, the invention provides a fluid machine and heat exchange equipment, wherein the heat exchange equipment comprises the fluid machine, and the fluid machine is the fluid machine.
Example 1
As shown in fig. 1 to 24, 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, 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 the assembly eccentricity of the crankshaft 10 and the cylinder liner 20 by an essence of aligning of the flange 50.
Specifically, as shown in fig. 6, the eccentric amounts of the two eccentric portions 11 are equal to e, as shown in fig. 7, the fitting eccentric amount between the crankshaft 10 and the cylinder liner 20 is e (since the cross groove structure 30 is coaxially provided with the cylinder liner 20, the fitting eccentric amount between the crankshaft 10 and the cross groove structure 30, that is, the fitting eccentric amount between the crankshaft 10 and the cylinder liner 20), and the flange 50 includes an upper flange 52 and a lower flange 53, as shown in fig. 8, 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. 2 to 7, the shaft body portion 12 of the crankshaft 10 is integrally formed, and the shaft body portion 12 has only one axial center. Thus, the one-time molding of the shaft body part 12 is facilitated, and the processing and manufacturing difficulty of the shaft body part 12 is reduced.
In an embodiment of the present application, the shaft portion 12 of the crankshaft 10 includes a first section and a second section connected along an axial direction thereof, the first section and the second section are coaxially disposed, and the two eccentric portions 11 are disposed on the first section and the second section, respectively.
Optionally, the first section is detachably connected to the second section. In this way, convenience in assembling and disassembling the crankshaft 10 is ensured.
As shown in fig. 2 to 7, 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. 2 to 7, 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. 2 to 7, 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. 9, the projection of the slider 40 in the axial direction of the through hole 41 has two relatively parallel straight line segments and an arc segment connecting the ends of the two straight line segments. The limiting channel 31 has a set of oppositely disposed first sliding surfaces in sliding contact with the slider 40, the slider 40 has a second sliding surface cooperating with the first sliding surfaces, the slider 40 has a pressing surface 42 facing the end of the limiting channel 31, the pressing surface 42 acts as the head of the slider 40, the two second sliding surfaces are connected by the pressing surface 42, and the pressing surface 42 faces the variable volume chamber 311. In this way, the projection of the second sliding surface of the slider 40 in the axial direction of the through hole 41 thereof is a straight line segment, while the projection of the pressing surface 42 of the slider 40 in the axial direction of the through hole 41 thereof is an arc segment.
Specifically, the pressing surface 42 is an arc surface, and the distance between the arc center of the arc surface and the center of the through hole 41 is equal to the eccentric amount of the eccentric portion 11. In fig. 9, 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. 9 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 the present embodiment, the enclosed space enclosed by the slide block 40, the limiting channel 31, the cylinder liner 20 and the upper flange 52 (or the lower flange 53) is the variable volume cavity 311, the pump body assembly 83 has 4 variable volume cavities 311 altogether, in the process of rotating the crankshaft 10, the crankshaft 10 rotates 2 circles, and a single variable volume cavity 311 completes 1 air intake and exhaust process, and for the compressor, the crankshaft 10 rotates 2 circles to complete 4 air intake and exhaust processes in total.
Further, the closed space surrounded by the extrusion surface 42 of the head of the sliding block 40, the two side wall surfaces and the channel bottom surface of the limiting channel 31, the partial inner wall surface of the cylinder liner 20, and the partial surface of the upper flange 52 facing the cylinder liner 20 (or the partial surface of the lower flange 53 facing the cylinder liner 20) is the variable volume cavity 311.
As shown in fig. 10 to 15, the slider 40 rotates relative to the cylinder liner 20 while reciprocating in the limiting passage 31, in fig. 10 to 12, the variable volume chamber 311 increases in the process of rotating the slider 40 clockwise from 0 degrees to 180 degrees, the variable volume chamber 311 communicates with the suction chamber 23 of the cylinder liner 20 in the process of increasing the variable volume chamber 311, when the slider 40 rotates to 180 degrees, the volume of the variable volume chamber 311 reaches the maximum value, the variable volume chamber 311 is separated from the suction chamber 23 at this time, thereby completing the suction operation, in fig. 13 to 15, the variable volume chamber 311 decreases in the process of continuing to rotate the slider 40 clockwise from 180 degrees to 360 degrees, the slider 40 compresses the gas in the variable volume chamber 311, when the slider 40 rotates to the variable volume chamber 311 communicates with the compression exhaust port 22, and when the gas in the variable volume chamber 311 reaches the exhaust pressure, the exhaust valve plate of the exhaust valve assembly opens, and the exhaust operation starts until the next cycle is entered after the compression is completed.
As shown in fig. 10 to 15, with the point marked with M as the reference point for the relative movement of the slider 40 and the crankshaft 10, fig. 11 shows a process in which the slider 40 rotates clockwise from 0 degrees to 180 degrees, the angle of rotation of the slider 40 is θ1, the corresponding angle of rotation of the crankshaft 10 is 2θ1, fig. 13 shows a process in which the slider 40 continues to rotate clockwise from 180 degrees to 360 degrees, the angle of rotation of the slider 40 is 180 ° +θ2, the corresponding angle of rotation of the crankshaft 10 is 360 ° +2θ2, fig. 14 shows a process in which the slider 40 continues to rotate clockwise from 180 degrees to 360 degrees, and the variable volume chamber 311 communicates with the compression exhaust port 22, the angle of rotation of the slider 40 is 180 ° +θ3, the corresponding angle of rotation of the crankshaft 10 is 360 ° +2θ3, that is, the slider 40 rotates 1 turn, and the corresponding crankshaft 10 rotates 2 turns, wherein θ1< θ2< θ3.
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 problem of how to reduce the exhaust loss, the application reduces the exhaust loss of the compressor by exhausting the air at the side of the cylinder sleeve 20, and specifically comprises the following steps:
As shown in fig. 1 to 24 and 34, two flanges 50 are respectively arranged at two axial ends of the cylinder sleeve 20, at least one flange 50 of the two flanges 50 is provided with an exhaust passage 51, wherein two exhaust ports 22 are arranged on the side wall surface of the cylinder sleeve 20, the two exhaust ports 22 are arranged at intervals along the axial direction of the cylinder sleeve 20, the two exhaust ports 22 are communicated with the exhaust passage 51, the cross section area of the hole section of the exhaust port 22 is S1, and the volume of a single variable volume cavity 311 is V1, wherein, the volume is more than or equal to 750 and less than or equal to V1/s1 is less than or equal to 3300.
The exhaust channel 51 is formed in at least one flange 50 of the two flanges 50, two exhaust ports 22 are formed in the side wall surface of the cylinder sleeve 20, the two exhaust ports 22 are arranged at intervals along the axial direction of the cylinder sleeve 20 and are communicated with the exhaust channel 51, the cross section area of the hole section of the exhaust port 22 is S1, the volume of the single variable volume cavity 311 is V1, wherein the volume is equal to or less than 750 and equal to or less than V1/S1 and equal to or less than 3300, and therefore, the exhaust reliability of the fluid machinery is ensured, the exhaust loss of the fluid machinery is reduced, and the efficiency of the fluid machinery is improved.
Further, the unit of S1 is square millimeter, and the unit of V1 is cubic millimeter.
In the present application, the value range of the ratio V1/S1 is the ratio of the numerical values, and the values are the same without units, and in addition, since the volume of the single variable volume chamber 311 is a variable value, the ratio range of V1 at the maximum in the present application is 750+.v1/s1+.3300.
As shown in fig. 34, COP refers to the performance of the compressor, i.e., the ratio of the output cooling capacity or heating capacity to the power consumed by the compressor.
In the present application, as shown in fig. 24, the cross section of the sliding block 40 in the sliding direction is S, and as shown in fig. 19, the assembly eccentricity of the cross groove structure 30 is e, and according to the compressor operation principle, it can be obtained that the volume v1=4es of the single variable volume chamber 311, the working volume of the whole compressor is V, and v=4v1=16es, that is, the displacement V of the compressor is 16eS, in cubic millimeters.
As shown in fig. 16 and 21, the positions of the two exhaust ports 22 in the circumferential direction of the cylinder liner 20 coincide.
As shown in fig. 2, 9 and 17, 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, and the exhaust port 22 is disposed in an angular range of (arccos (2R/B) to 2× arccos 2R/B) in the circumferential direction of the cylinder liner 20, where R is the inner radius of the cylinder liner 20 and B is the distance between the two relatively parallel straight line segments of the projection of the slider 40 in the axial direction of the through hole 41. Thus, by reasonably optimizing the arrangement position of the exhaust port 22 in the circumferential direction of the cylinder liner 20, it is advantageous to avoid over-compression or under-compression of the compressor, and the angle range θ in fig. 17 is (arccos (2R/B) to 2× arccos 2R/B), that is, the exhaust port 22 can be arranged in the above-mentioned range in the circumferential direction of the cylinder liner 20.
As shown in fig. 10 to 18, the outer wall of the cylinder sleeve 20 is provided with an exhaust cavity 25, the exhaust port 22 is communicated to the exhaust cavity 25 by the inner wall of the cylinder sleeve 20, the fluid machine further comprises exhaust valve components, the exhaust valve components are arranged in the exhaust cavity 25 and correspond to the exhaust ports 22, the exhaust valve components are in two groups, and the two groups of exhaust valve components are respectively correspond to the two exhaust ports 22. In this way, the exhaust cavity 25 is used for accommodating the exhaust valve assembly, so that the occupied space of the exhaust valve assembly is effectively reduced, components are reasonably arranged, and the space utilization rate of the cylinder sleeve 20 is improved.
As shown in fig. 10 to 18, a communication hole 26 is further provided in the axial end surface of the cylinder liner 20, the communication hole 26 communicates with the exhaust chamber 25, and the communication hole 26 communicates with the exhaust passage 51. In this way, the exhaust reliability of the cylinder liner 20 is ensured.
As shown in fig. 16 and 21, the number of the exhaust chambers 25 is two, the two exhaust chambers 25 are arranged at intervals along the axial direction of the cylinder liner 20, and the two exhaust chambers 25 are arranged in one-to-one correspondence and communicate with the two exhaust ports 22. In this way, it is advantageous to reduce the throttling loss, thereby improving the performance of the compressor.
As shown in fig. 16, the two exhaust chambers 25 communicate through an exhaust communication hole 28, and the exhaust communication hole 28 extends in the axial direction of the cylinder liner 20. In this way, the communication reliability of the two exhaust chambers 25 is ensured.
Further, as shown in fig. 2, the exhaust chamber 25 penetrates through the outer wall surface of the cylinder liner 20, and the fluid machine further includes an exhaust cover plate connected to the cylinder liner 20 and sealing the exhaust chamber 25. In this way, the vent cover plate 70 functions to isolate the variable volume chamber 311 from the external space of the pump body assembly 83.
Optionally, the exhaust cover plate 70 is secured to the cylinder liner 20 by fasteners.
Optionally, the fastener is a screw.
Optionally, the outer contour of the vent flap 70 is adapted to the outer contour of the vent chamber 25.
As shown in fig. 18, the distance between the plane of the end of the exhaust port 22, which is in communication with the exhaust chamber 25, and the axis of the cylinder liner 20 is K, and the inner radius of the cylinder liner 20 is R, wherein 1mm +.k-R +.5 mm. Therefore, the value range of K-R is reasonably optimized, the reliability requirement of the compressor is met, on one hand, the problem that the thickness of the cylinder sleeve wall at the exhaust port 22 is thinner due to the fact that K-R is too small, so that the strength of the cylinder sleeve wall at the exhaust port 22 is insufficient is avoided, the cylinder sleeve wall at the exhaust port 22 is easily broken due to high-frequency impact of a valve plate in a subsequent exhaust valve assembly, and on the other hand, the problem that the thickness of the cylinder sleeve wall at the exhaust port 22 is too thick due to the fact that K-R is too large is also avoided, the strength of the cylinder sleeve wall at the exhaust port 22 can meet the requirement, but the clearance volume is increased, and the energy efficiency of the compressor is reduced.
As shown in fig. 20 and 21, the cross-sectional area of the exhaust chamber 25 in the axial direction of the cylinder liner 20 is S2, the height of the single exhaust chamber 25 in the axial direction of the cylinder liner 20 is M, and the displacement of the fluid machine is V, wherein 0.5+.mxs2/v+.5. Thus, by reasonably optimizing the range of the ratio of the volume of the discharge chamber 25 to the displacement V of the compressor (fluid machine), it is ensured that the discharge chamber 25 can function to reduce the discharge noise and reduce the oil circulation rate at the time of high-speed operation of the compressor, where S2 is in square millimeters and M is in mm.
It should be noted that in this embodiment, as shown in fig. 22 and 23, another alternative embodiment may be provided, in which, an exhaust cavity 25 is formed on an outer wall of the cylinder liner 20, a boss structure 29 is disposed on a cavity wall surface of the exhaust cavity 25, and the exhaust port 22 is penetrated from an inner wall of the cylinder liner 20 to the boss structure 29 and is communicated with the exhaust cavity 25. Like this, boss structure 29 is the structural style of evagination, is favorable to reducing the discharge valve block of discharge valve subassembly and leads to opening the loss because of lubricating oil viscosity through setting up boss structure 29.
Further, as shown in fig. 23, the thickness of the boss structure 29 in the extending direction of the exhaust port 22 is N, where 0.05 mm+.n+.3 mm. In this way, on the one hand, the wall thickness of the cylinder liner at the exhaust port 22 is increased to ensure that the strength of the cylinder liner wall is sufficient, and on the other hand, the opening loss of the exhaust valve plate of the exhaust valve assembly can be reduced.
As shown in fig. 2,10 to 19, the cylinder liner 20 has a radial suction hole 21 and a suction chamber 23, and the suction chamber 23 communicates with the radial suction hole 21. In this way, it is ensured that the suction chamber 23 can store a large amount of gas, so that the variable volume chamber 311 can be filled with suction gas, thereby enabling the compressor to be capable of sucking gas in a sufficient amount, and when the suction gas is insufficient, the stored gas can be timely supplied to the variable volume chamber 311, so as to ensure the compression efficiency of the compressor.
Alternatively, the suction chambers 23 are cavities formed by hollowing out the inner wall surface of the cylinder sleeve 20 along the radial direction, and the number of the suction chambers 23 can be 1 or 2.
Specifically, the suction chamber 23 extends a first preset distance around the circumference of the inner wall surface of the cylinder liner 20 to constitute an arc-shaped suction chamber 23. In this way, it is ensured that the volume of the suction chamber 23 is sufficiently large to store a large amount of gas.
As shown in fig. 2, 10 to 19, 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 the radial air suction holes 21 are communicated with the 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, as shown in fig. 2, the suction communication chamber 24 extends a second predetermined distance in the axial direction of the cylinder liner 20, and at least one end of the suction communication chamber 24 penetrates through the axial end face of the cylinder liner 20. Thus, the air suction communication cavity 24 is conveniently formed on the end face of the cylinder sleeve 20, and the processing convenience of the air suction communication cavity 24 is ensured.
In the present embodiment, as shown in fig. 2, the upper flange 52 is provided with an exhaust passage 51, and the two exhaust ports 22 are communicated with the exhaust passage 51 through the exhaust chamber 25 and the communication hole 26.
Example two
It should be noted that the difference between the present embodiment and the first embodiment is that, as shown in fig. 25, the upper flange 52 and the lower flange 53 are both provided with the exhaust passage 51, and the exhaust port 22 on the upper side of the cylinder liner 20 is communicated with the exhaust passage 51 on the upper flange 52, and the exhaust port 22 on the lower side of the cylinder liner 20 is communicated with the exhaust passage 51 on the lower flange 53.
Example III
It should be noted that the difference between the present embodiment and the first embodiment is that, as shown in fig. 26, the cylinder liner 20 has two radial air intake holes 21, and the two radial air intake holes 21 are disposed at intervals along the axial direction of the cylinder liner 20, and the two radial air intake holes 21 are respectively communicated with the air intake chambers 23 on the corresponding sides.
Example IV
It should be noted that the difference between the present embodiment and the second embodiment is that, as shown in fig. 27, the cylinder liner 20 has two radial air intake holes 21, and the two radial air intake holes 21 are disposed at intervals along the axial direction of the cylinder liner 20, and the two radial air intake holes 21 are respectively communicated with the air intake chambers 23 on the corresponding sides.
Of course, in an embodiment of the present application, the upper flange 52 and the lower flange 53 may be used to suck air through the flanges 50, or one flange 50 of the two flanges 50 may be used to suck air together with the cylinder liner 20.
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 (14)
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 (311), the variable volume cavity (311) is located 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 two axial ends of the cylinder sleeve (20), and at least one flange (50) of the two flanges (50) is provided with an exhaust channel (51);
two exhaust ports (22) are formed in the side wall surface of the cylinder sleeve (20), the two exhaust ports (22) are arranged at intervals along the axial direction of the cylinder sleeve (20), and the two exhaust ports (22) are communicated with the exhaust channel (51);
the cross section of the hole section of the exhaust port (22) is S1, the volume of the single variable-volume cavity (311) is V1, wherein 750 is less than or equal to V1/S1 is less than or equal to 3300, and the value range of V1/S1 is the ratio range when V1 is at the maximum value.
2. A fluid machine according to claim 1, wherein the positions of both exhaust ports (22) in the circumferential direction of the cylinder liner (20) coincide.
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 exhaust port (22) is arranged in an angle range of (arccos (2R/B) -2× arccos (2R/B)) in the circumferential direction of the cylinder sleeve (20), wherein R is the inner circle radius of the cylinder sleeve (20), and B is the distance between two relatively parallel straight line segments of the projection of the sliding block (40) in the axial direction of the through hole (41).
4. The fluid machine according to claim 1, wherein the outer wall of the cylinder sleeve (20) is provided with an exhaust cavity (25), the exhaust port (22) is communicated to the exhaust cavity (25) by the inner wall of the cylinder sleeve (20), the fluid machine further comprises exhaust valve assemblies, the exhaust valve assemblies are arranged in the exhaust cavity (25) and correspond to the exhaust ports (22), the exhaust valve assemblies are two groups, and the two groups of exhaust valve assemblies are respectively correspond to the two exhaust ports (22).
5. The fluid machine according to claim 4, characterized in that a communication hole (26) is further provided on an axial end face of the cylinder liner (20), the communication hole (26) being in communication with the exhaust chamber (25), the communication hole (26) being in communication with the exhaust passage (51).
6. The fluid machine according to claim 4, wherein the number of the exhaust chambers (25) is two, the two exhaust chambers (25) are arranged at intervals along the axial direction of the cylinder sleeve (20), and the two exhaust chambers (25) are arranged and communicated with the two exhaust ports (22) in a one-to-one correspondence.
7. The fluid machine according to claim 6, wherein two of the exhaust chambers (25) are communicated through an exhaust communication hole (28), the exhaust communication hole (28) extending in an axial direction of the cylinder liner (20).
8. The fluid machine according to claim 4, wherein the distance between the plane of the end of the exhaust port (22) communicating with the exhaust chamber (25) and the axis of the cylinder liner (20) is K, and the inner radius of the cylinder liner (20) is R, wherein 1mm +.k-R +.5 mm.
9. The fluid machine according to claim 4, wherein the chamber cross-sectional area of the exhaust chamber (25) in the axial direction of the cylinder liner (20) is S2, the height of the exhaust chamber (25) in the axial direction of the cylinder liner (20) alone is M, and the displacement of the fluid machine is V, wherein 0.5+.ltoreq.m x S2)/v+.ltoreq.5.
10. The fluid machine according to claim 1, wherein an exhaust cavity (25) is formed in the outer wall of the cylinder sleeve (20), a boss structure (29) is arranged on the cavity wall surface of the exhaust cavity (25), and the exhaust port (22) penetrates through the boss structure (29) from the inner wall of the cylinder sleeve (20) and is communicated with the exhaust cavity (25).
11. The fluid machine according to claim 10, wherein the thickness of the boss structure (29) in the extension direction of the exhaust port (22) is N, wherein 0.05mm +.n+.3 mm.
12. The fluid machine according to claim 4 or 10, characterized in that the exhaust chamber (25) penetrates to the outer wall surface of the cylinder liner (20), the fluid machine further comprising an exhaust cover plate, which is connected to the cylinder liner (20) and seals the exhaust chamber (25).
13. The fluid machine according to any one of claims 1 to 11, 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.
14. 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 13.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
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| CN202210568373.3A CN117145773B (en) | 2022-05-23 | 2022-05-23 | Fluid machinery and heat exchange equipment |
| PCT/CN2022/140983 WO2023226414A1 (en) | 2022-05-23 | 2022-12-22 | Fluid machine and heat exchange device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN202210568373.3A CN117145773B (en) | 2022-05-23 | 2022-05-23 | Fluid machinery and heat exchange equipment |
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| CN117145773A CN117145773A (en) | 2023-12-01 |
| CN117145773B true CN117145773B (en) | 2025-11-25 |
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| WO (1) | WO2023226414A1 (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104963861A (en) * | 2015-07-02 | 2015-10-07 | 广东美芝制冷设备有限公司 | Compressing mechanism for rotary compressor and rotary compressor with compressing mechanism |
| CN107120275A (en) * | 2017-06-29 | 2017-09-01 | 广东美芝制冷设备有限公司 | Compression mechanism and rotary compressor |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU462784B2 (en) * | 1972-05-18 | 1975-07-10 | General Motors Corporation | Radial compressors |
| JPS59155580A (en) * | 1983-02-25 | 1984-09-04 | Hitachi Ltd | Capacity control type compressor |
| DE4228639A1 (en) * | 1992-08-28 | 1994-03-03 | Josef Gail | Cylinder machine |
| JP2004019521A (en) * | 2002-06-14 | 2004-01-22 | Nippon Soken Inc | Displacement type fluid machine |
| 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 |
| CN205064265U (en) * | 2015-08-07 | 2016-03-02 | 珠海格力节能环保制冷技术研究中心有限公司 | Fluid machinery and indirect heating equipment |
| 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 |
| CN106704182B (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 |
| CN206943012U (en) * | 2017-06-29 | 2018-01-30 | 南京奥特佳新能源科技有限公司 | Rotary Vane Motor Vehicle Air-Conditioning Compressor exhaust valve plate mounting structure |
| CN107781164B (en) * | 2017-10-11 | 2024-10-15 | 重庆凌达压缩机有限公司 | Compressor bearing with adjustable center distance of exhaust port and 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 |
-
2022
- 2022-05-23 CN CN202210568373.3A patent/CN117145773B/en active Active
- 2022-12-22 WO PCT/CN2022/140983 patent/WO2023226414A1/en not_active Ceased
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104963861A (en) * | 2015-07-02 | 2015-10-07 | 广东美芝制冷设备有限公司 | Compressing mechanism for rotary compressor and rotary compressor with compressing mechanism |
| CN107120275A (en) * | 2017-06-29 | 2017-09-01 | 广东美芝制冷设备有限公司 | Compression mechanism and rotary compressor |
Also Published As
| Publication number | Publication date |
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| WO2023226414A1 (en) | 2023-11-30 |
| CN117145773A (en) | 2023-12-01 |
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