CN112460021A - Pump body subassembly, rotor compressor and air conditioner - Google Patents

Pump body subassembly, rotor compressor and air conditioner Download PDF

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Publication number
CN112460021A
CN112460021A CN202011401662.1A CN202011401662A CN112460021A CN 112460021 A CN112460021 A CN 112460021A CN 202011401662 A CN202011401662 A CN 202011401662A CN 112460021 A CN112460021 A CN 112460021A
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CN
China
Prior art keywords
roller
bearing
pump body
crankshaft
body assembly
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202011401662.1A
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Chinese (zh)
Inventor
柯达俊
巩庆霞
吴健
尹雪峰
罗惠芳
邓罡
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Zhuhai Gree Energy Saving Environmental Protection Refrigeration Technology Research Center Co Ltd
Original Assignee
Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
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Application filed by Gree Green Refrigeration Technology Center Co Ltd of Zhuhai filed Critical Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Priority to CN202011401662.1A priority Critical patent/CN112460021A/en
Publication of CN112460021A publication Critical patent/CN112460021A/en
Pending legal-status Critical Current

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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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with or adaptation to specific driving engines or motors
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C2240/00—Components
    • F04C2240/10—Stators
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Abstract

The invention provides a pump body assembly, a rotor compressor and an air conditioner, wherein the pump body assembly comprises an air cylinder, a roller structure and a crankshaft, wherein the roller structure is arranged in a compression cavity of the air cylinder; when the roller structure is a roller, the displacement V of the pump body component and the bearing area S of the roller5Ratio of (V/S)5Is in the range of 29 to 36; when the roller structure consists of two rollers, the two rollers are respectively a first roller and a second roller, and the first roller is positioned on one side of the second roller, which is close to the power input end of the crankshaft; displacement V of pump body assembly and bearing area S of first roller1Ratio of (V/S)1Value range ofIs 56 to 63; discharge volume V of pump body assembly and bearing area S of second roller2Ratio of (V/S)2Is in the range of 60 to 70. The pump body assembly solves the problem that the rotor compressor in the prior art is low in energy efficiency.

Description

Pump body subassembly, rotor compressor and air conditioner
Technical Field
The invention relates to the field of rotor compressors, in particular to a pump body assembly, a rotor compressor and an air conditioner.
Background
The rotor compressor has the advantages of small volume, light weight, low manufacturing cost and the like, and has wide application in the fields of household air conditioners, commercial air conditioners and the like.
There is also a constant effort in the art to improve the energy efficiency of the rotary compressor and thereby reduce the energy consumption of the air conditioner. However, the energy efficiency of the current rotor compressor is still low and is difficult to be further improved.
Disclosure of Invention
The invention mainly aims to provide a pump body assembly, a rotor compressor and an air conditioner, and aims to solve the problem that the rotor compressor in the prior art is low in energy efficiency.
In order to achieve the above object, according to one aspect of the present invention, there is provided a pump body assembly, including a cylinder, a roller structure installed in a compression cavity of the cylinder, and a crankshaft, wherein the roller structure is sleeved on the crankshaft to drive the roller structure to roll along an inner wall of the compression cavity through the crankshaft; when the roller structure is a roller, the displacement V of the pump body component and the bearing area S of the roller5Ratio of (V/S)5Is in the range of 29 to 36; when the roller structure consists of two rollers, the two rollers are respectively a first roller and a second roller, and the first roller is positioned on one side of the second roller, which is close to the power input end of the crankshaft; displacement V of pump body assembly and bearing area S of first roller1Ratio of (V/S)1The value range of (1) is 56 to 63; discharge volume V of pump body assembly and bearing area S of second roller2Ratio of (V/S)2The value range of (a) is 60 to 70; the displacement V of the pump body assembly is the displacement of the pump body assembly in one working cycle; bearing area S of roller5The area of the orthographic projection of the contact surface of the roller and the crankshaft in a first plane is vertical to the direction of the pressure applied to the roller by the crankshaft; bearing area S of first roller1The area of the orthographic projection of the contact surface of the first roller and the crankshaft in a second plane is provided, and the second plane is vertical to the direction of the pressure applied by the crankshaft to the first roller; bearing area S of second roller2The area of the orthographic projection of the contact surface of the second roller and the crankshaft in a third plane is perpendicular to the direction of the pressure applied by the crankshaft to the second roller.
Further, when the roller structure is a roller, the contact surface of the roller and the crankshaft is a cylindrical surface, and the diameter of the cylindrical surface is d5Height of the cylindrical surface is h5(ii) a Bearing area S of roller5＝d5×h5(ii) a When the roller structure consists of two rollers, the contact surface of the first roller and the crankshaft is a first cylindrical surface, and the contact surface of the second roller and the crankshaft is a second cylindrical surface; the diameter of the first cylindrical surface is d1The height of the first cylindrical surface is h1The diameter of the second cylindrical surface is d2The height of the second cylindrical surface is h2(ii) a Bearing area S of first roller1＝d1×h1Bearing area S of the second roller2＝d2×h2。
Further, when the roller structure is composed of two rollers, the displacement V of the pump body assembly and the bearing area S of the first roller1Ratio of (V/S)1Is in the range of 56 to 60; discharge volume V of pump body assembly and bearing area S of second roller2Ratio of (V/S)2Is in the range of 60 to 66.
Further, when the roller structure is composed of two rollers, the displacement V of the pump body assembly and the bearing area S of the first roller1Ratio of (V/S)1The value range of (a) is 60 to 63; discharge volume V of pump body assembly and bearing area S of second roller2Ratio of (V/S)2Is in the range of 66 to 70.
Further, the pump body assembly comprises a main bearing and an auxiliary bearing, and the main bearing and the auxiliary bearing are correspondingly arranged on the cylinderTo support the crankshaft via the main and auxiliary bearings; the main bearing is positioned on one side of the auxiliary bearing close to the power input end of the crankshaft; when the roller structure is a roller, the discharge volume V of the pump body assembly and the bearing area S of the main bearing6Ratio of (V/S)6Is in the range of 22 to 27; displacement V of pump body assembly and bearing area S of auxiliary bearing7Ratio of (V/S)7Is in the range of 48 to 57; wherein the bearing area S of the main bearing6The area of the orthographic projection of the contact surface of the main bearing and the crankshaft in a fourth plane is provided, and the fourth plane is vertical to the direction of the pressure force applied to the crankshaft by the main bearing; bearing area S of the secondary bearing7The area of the orthographic projection of the contact surface of the auxiliary bearing and the crankshaft in a fifth plane is perpendicular to the direction of the pressure applied to the crankshaft by the auxiliary bearing.
Further, the pump body assembly comprises a main bearing and an auxiliary bearing, wherein the main bearing and the auxiliary bearing are correspondingly arranged at two opposite ends of the cylinder so as to support the crankshaft through the main bearing and the auxiliary bearing; the main bearing is positioned on one side of the auxiliary bearing close to the power input end of the crankshaft; when the roller structure consists of a first roller and a second roller, the displacement V of the pump body assembly and the bearing area S of the main bearing3Ratio of (V/S)3Is in the range of 37 to 44; displacement V of pump body assembly and bearing area S of auxiliary bearing4Ratio of (V/S)4Ranges from 76 to 88; wherein the bearing area S of the main bearing3The area of the orthographic projection of the contact surface of the main bearing and the crankshaft in a fourth plane is provided, and the fourth plane is vertical to the direction of the pressure force applied to the crankshaft by the main bearing; bearing area S of the secondary bearing4The area of the orthographic projection of the contact surface of the auxiliary bearing and the crankshaft in a fifth plane is perpendicular to the direction of the pressure applied to the crankshaft by the auxiliary bearing.
Further, the discharge volume V of the pump body assembly and the bearing area S of the main bearing3Ratio of (V/S)3Is in the range of 37 to 41; displacement V of pump body assembly and bearing area S of auxiliary bearing4Ratio of (V/S)4Is in the range of 76 to 80.
Further, of pump body assembliesDischarge volume V and bearing area S of main bearing3Ratio of (V/S)3Is in the range of 41 to 44; displacement V of pump body assembly and bearing area S of auxiliary bearing4Ratio of (V/S)4Is in the range of 80 to 88.
Furthermore, the contact surface of the main bearing and the crankshaft is a third cylindrical surface, and the contact surface of the auxiliary bearing and the crankshaft is a fourth cylindrical surface; the diameter of the third cylindrical surface is d3The height of the third cylindrical surface is h3The diameter of the fourth cylindrical surface is d4The height of the fourth cylindrical surface is h4(ii) a Bearing area S of the main bearing3＝d3×h3Bearing area S of the secondary bearing4＝d4×h4。
According to a second aspect of the present invention, there is provided a rotary compressor comprising: the pump body component is the pump body component; the motor assembly is used for driving a crankshaft of the pump body assembly to rotate; a liquid separator for separating the gaseous refrigerant from the liquid refrigerant; the liquid separator is connected with an air suction port of the cylinder of the pump body assembly to supply gaseous refrigerant to the cylinder.
According to a third aspect of the present invention, there is provided an air conditioner including the above-described rotary compressor.
The pump body assembly adopting the technical scheme of the invention comprises an air cylinder, a roller structure and a crankshaft, wherein the roller structure is arranged in a compression cavity of the air cylinder; when the roller structure is a roller, the displacement V of the pump body component and the bearing area S of the roller5Ratio of (V/S)5Is in the range of 29 to 36; when the roller structure consists of two rollers, the two rollers are respectively a first roller and a second roller, and the first roller is positioned on one side of the second roller, which is close to the power input end of the crankshaft; displacement V of pump body assembly and bearing area S of first roller1Ratio of (V/S)1The value range of (1) is 56 to 63; discharge volume V of pump body assembly and bearing area S of second roller2Ratio of (V/S)2The value range of (a) is 60 to 70; wherein the pump body assemblyThe displacement V is the displacement of the pump body assembly in one working cycle; bearing area S of roller5The area of the orthographic projection of the contact surface of the roller and the crankshaft in a first plane is vertical to the direction of the pressure applied to the roller by the crankshaft; bearing area S of first roller1The area of the orthographic projection of the contact surface of the first roller and the crankshaft in a second plane is provided, and the second plane is vertical to the direction of the pressure applied by the crankshaft to the first roller; bearing area S of second roller2The area of the orthographic projection of the contact surface of the second roller and the crankshaft in a third plane is perpendicular to the direction of the pressure applied by the crankshaft to the second roller. By designing the bearing area (effective stress area) of the contact surface of the roller structure and the crankshaft, aiming at the pump body assembly with a single-roller structure, the displacement V of the pump body assembly and the bearing area S of a roller are enabled to be equal5Ratio of (V/S)5Is in the range of 29 to 36; aiming at the pump body component with a double-roller structure, the discharge volume V of the pump body component and the bearing area S of the first roller are enabled to be1Ratio of (V/S)1The value range of (1) is 56 to 63; in particular the displacement V of the pump body assembly and in particular the bearing area S of the second roller2Ratio of (V/S)2Is in the range of 60 to 70. Through the arrangement, the area of the contact surface of the crankshaft and the roller structure is in a better range, an oil film with proper thickness can be formed between the crankshaft and the roller structure, the lubricating effect is improved, the friction power loss of the pump body assembly is reduced, and the energy efficiency of the rotor compressor is improved.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 shows a schematic cross-sectional structural view of a first embodiment of a pump block assembly according to the present invention;
FIG. 2 shows a schematic cross-sectional structural view of a second embodiment of the pump block assembly according to the present invention;
FIG. 3 is a schematic diagram showing the mating relationship of the cylinders, roller structures, and crankshaft of an embodiment of the pump block assembly according to the present invention;
FIG. 4 shows a schematic structural view of a crankshaft of an embodiment of a pump block assembly according to the present invention;
fig. 5 shows a schematic structural view of an embodiment of a rotary compressor according to the present invention.
Wherein the figures include the following reference numerals:
1. a cylinder; 2. a roller structure; 21. a first drum; 22. a second drum; 3. a crankshaft; 31. a shaft body; 32. a first eccentric portion; 33. a second eccentric portion; 4. a main bearing; 5. a secondary bearing; 6. sliding blades; 100. a pump body assembly; 200. a motor assembly; 300. a liquid distributor.
Detailed Description
It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
The applicant has studied and found that one of the most important causes of the low energy efficiency of the existing rotary compressors is the friction inside the pump body assembly of the rotary compressor. The applicant finds that most of friction inside the pump body assembly of the rotor compressor is concentrated at the contact surface (the eccentric bearing) of the crankshaft 3 and the roller structure 2, and the reduction of the friction at the position is beneficial to reducing the friction power loss inside the pump body assembly and improving the energy efficiency of the rotor compressor.
Referring to fig. 1 to 4, the present invention provides a pump assembly, which includes a cylinder 1, a roller structure 2 installed in a compression cavity of the cylinder 1, and a crankshaft 3, wherein the roller structure 2 is sleeved on the crankshaft 3 to drive the roller structure 2 to roll along an inner wall of the compression cavity through the crankshaft 3; when the roller structure 2 is a roller, the displacement V of the pump body assembly and the bearing area S of the roller5Ratio of (V/S)5Is in the range of 29 to 36; when the roller structure 2 is composed of two rollers, which are a first roller 21 and a second roller 22, respectively, the first roller 21 is located on one side of the second roller 22 close to the power input end of the crankshaft 3; the displacement V of the pump body assembly and the bearing area S of the first roller 211Ratio of (A to (B)Value V/S1The value range of (1) is 56 to 63; the displacement V of the pump body assembly and the bearing area S of the second roller 222Ratio of (V/S)2The value range of (a) is 60 to 70; the displacement V of the pump body assembly is the displacement of the pump body assembly in one working cycle; bearing area S of roller5The area of the orthographic projection of the contact surface of the roller and the crankshaft 3 in a first plane is vertical to the direction of the pressure applied to the roller by the crankshaft 3; bearing area S of first roller 211Is the orthographic projection area of the contact surface of the first roller 21 and the crankshaft 3 in a second plane, and the second plane is vertical to the direction of the pressure applied to the first roller 21 by the crankshaft 3; bearing area S of the second roller 222The area of the orthogonal projection of the contact surface of the second drum 22 and the crankshaft 3 in the third plane is perpendicular to the direction of the pressure applied by the crankshaft 3 to the second drum 22.
The pump body assembly comprises a cylinder 1, a roller structure 2 and a crankshaft 3, wherein the roller structure 2 is arranged in a compression cavity of the cylinder 1, and the roller structure 2 is sleeved on the crankshaft 3 so as to drive the roller structure 2 to roll along the inner wall of the compression cavity through the crankshaft 3; when the roller structure 2 is a roller, the displacement V of the pump body assembly and the bearing area S of the roller5Ratio of (V/S)5Is in the range of 29 to 36; when the roller structure 2 is composed of two rollers, which are a first roller 21 and a second roller 22, respectively, the first roller 21 is located on one side of the second roller 22 close to the power input end of the crankshaft 3; the displacement V of the pump body assembly and the bearing area S of the first roller 211Ratio of (V/S)1The value range of (1) is 56 to 63; the displacement V of the pump body assembly and the bearing area S of the second roller 222Ratio of (V/S)2The value range of (a) is 60 to 70; the displacement V of the pump body assembly is the displacement of the pump body assembly in one working cycle; bearing area S of roller5The area of the orthographic projection of the contact surface of the roller and the crankshaft 3 in a first plane is vertical to the direction of the pressure applied to the roller by the crankshaft 3; bearing area S of first roller 211Is the orthographic projection area of the contact surface of the first roller 21 and the crankshaft 3 in a second plane, and the second plane is vertical to the direction of the pressure applied to the first roller 21 by the crankshaft 3;bearing area S of the second roller 222The area of the orthogonal projection of the contact surface of the second drum 22 and the crankshaft 3 in the third plane is perpendicular to the direction of the pressure applied by the crankshaft 3 to the second drum 22. By designing the bearing area (effective stress area) of the contact surface of the roller structure 2 and the crankshaft 3, aiming at the pump body assembly of a single-roller structure, the displacement V of the pump body assembly and the bearing area S of a roller are enabled to be equal5Ratio of (V/S)5Is in the range of 29 to 36; aiming at the pump body component with a double-roller structure, the discharge volume V of the pump body component and the bearing area S of the first roller 21 are enabled1Ratio of (V/S)1The value range of (1) is 56 to 63; in particular the displacement V of the pump body assembly and in particular the bearing area S of the second roller 222Ratio of (V/S)2Is in the range of 60 to 70. Through the arrangement, the area of the contact surface of the crankshaft 3 and the roller structure 2 is in a better range, an oil film with proper thickness can be formed between the crankshaft and the roller structure, the lubricating effect is improved, the friction power loss of the pump body assembly is reduced, and the energy efficiency of the rotor compressor is improved.
The bearing area of the contact surface between the roller structure 2 and the crankshaft 3 in the conventional rotor compressor is not designed, and generally, the larger the area is, the more stable the supporting effect of the crankshaft 3 on the roller structure 2 is, and the better the lubricating effect is, so that the values of the conventional rotor compressor are obviously smaller than those of the present application. That is, for a pump body assembly of a single roller, the displacement V of the pump body assembly and in particular the bearing area S of the roller5Ratio of (V/S)5Are less than 29. For a double-roller pump assembly, the displacement V of the pump assembly and in particular the bearing area S of the first roller 211Ratio of (V/S)1Are both less than 56, the displacement V of the pump body assembly thereof and in particular the bearing area S of the second roller 222Are all less than 60.
In the present application, the applicant found that the larger the bearing area of the contact surface between the roller structure 2 and the crankshaft 3 is, the better, and that if the bearing area exceeds a certain range, the thickness of the oil film between the roller structure 2 and the crankshaft 3 increases, and the adhesive force generated thereby also increases, and conversely, the friction loss between the roller structure 2 and the crankshaft 3 increases. When the area is smaller, the thickness of the oil film is reduced to be small, and the friction power consumption generated by metal contact is increased. Through the pump body subassembly to single cylinder and twin drum in this application, design this bearing area, can guarantee that the thickness of the oil film between pump body subassembly during operation bent axle 3 and the roller structure 2 is in the scope of preferred, improve lubricated effect, reduce pump body subassembly's frictional power loss, improve rotor compressor's efficiency.
The displacement V of the pump assembly refers to the volume of fluid that can be conveyed by one cycle of operation of the pump assembly, and as shown in fig. 3, the value of the displacement V is equal to the volume of a crescent space E defined between the inner wall surface of the cylinder 1 and the outer wall surface of the roller structure 2.
Specifically, when the roller structure 2 is two rollers, as shown in fig. 2, the cylinder 1 is a split structure, that is, includes two cylinder blocks, the two rollers are respectively and correspondingly installed in the two cylinder blocks, and the displacement V of the pump body assembly is equal to the sum of the displacements of the two cylinder blocks.
As shown in fig. 3, the principle of compression of the pump assembly on the refrigerant is the same as that of a rotor compressor in the related art, that is, the pump assembly further includes a sliding vane 6 and an elastic member, the sliding vane 6 and the elastic member are both mounted on the cylinder 1, the sliding vane 6 is always in contact with the surface of the roller structure 2 under the elastic action of the elastic member, when the roller structure 2 rolls along the inner wall of the compression cavity, the refrigerant is driven to be sucked into the compression cavity of the cylinder 1 through the suction port of the cylinder 1, and the refrigerant is compressed, so that the compressed refrigerant is discharged from the exhaust port of the cylinder 1.
As for the structure of the crankshaft 3, as shown in fig. 4, taking the case that the roller structure 2 is composed of two rollers as an example, the crankshaft 3 includes a shaft body 31, a first eccentric portion 32 and a second eccentric portion 33, the outer surfaces of the first eccentric portion 32 and the second eccentric portion 33 are both cylindrical surfaces, the axis of the first eccentric portion 32 is parallel (not coincident) with the axis of the shaft body 31, the axis of the second eccentric portion 33 is parallel (not coincident) with the axis of the shaft body 31, the first roller 21 is sleeved on the first eccentric portion 32, and the second roller 22 is sleeved on the second eccentric portion 33.
Specifically, when the roller structure 2 is a roller, the contact surface of the roller with the crankshaft 3Is a cylindrical surface with a diameter d5Height of the cylindrical surface is h5(ii) a Bearing area S of roller5＝d5×h5(ii) a When the roller structure 2 is composed of two rollers, the contact surface of the first roller 21 and the crankshaft 3 is a first cylindrical surface, and the contact surface of the second roller 22 and the crankshaft 3 is a second cylindrical surface; the diameter of the first cylindrical surface is d1The height of the first cylindrical surface is h1The diameter of the second cylindrical surface is d2The height of the second cylindrical surface is h2(ii) a Bearing area S of first roller 211＝d1×h1Bearing area S of the second roller 222＝d2×h2。
In particular, when the roller structure 2 consists of two rollers, the displacement V of the pump body assembly and the bearing area S of the first roller 211Ratio of (V/S)1Is in the range of 56 to 60; the displacement V of the pump body assembly and the bearing area S of the second roller 222Ratio of (V/S)2Is in the range of 60 to 66.
Through adopting above-mentioned setting, can guarantee on the basis of guaranteeing lubricated effect that pump body subassembly has higher discharge capacity, improve pump body subassembly's performance.
In particular, when the roller structure 2 consists of two rollers, the displacement V of the pump body assembly and the bearing area S of the first roller 211Ratio of (V/S)1The value range of (a) is 60 to 63; the displacement V of the pump body assembly and the bearing area S of the second roller 222Ratio of (V/S)2Is in the range of 66 to 70.
By adopting the arrangement, the lubricating effect between the crankshaft 3 and the roller structure 2 can be fully ensured, the friction power loss of the pump body assembly is reduced to a very small range, and the energy efficiency of the rotor compressor is improved.
Specifically, the pump body assembly comprises a main bearing 4 and a secondary bearing 5, wherein the main bearing 4 and the secondary bearing 5 are correspondingly arranged at two opposite ends of the cylinder 1 so as to support the crankshaft 3 through the main bearing 4 and the secondary bearing 5; the main bearing 4 is positioned on one side of the auxiliary bearing 5 close to the power input end of the crankshaft 3; when the roller structure 2 is a roller, the displacement V and the main shaft of the pump body componentBearing area S of bearing 46Ratio of (V/S)6Is in the range of 22 to 27; displacement V of pump body assembly and bearing area S of auxiliary bearing 57Ratio of (V/S)7Is in the range of 48 to 57; wherein the bearing area S of the main bearing 46The area of the orthographic projection of the contact surface of the main bearing 4 and the crankshaft 3 in a fourth plane is vertical to the direction of the pressure applied to the crankshaft 3 by the main bearing 4; bearing surface S of the secondary bearing 57The area of the orthogonal projection of the contact surface of the sub-bearing 5 and the crankshaft 3 in the fifth plane is perpendicular to the direction of the pressure applied by the sub-bearing 5 to the crankshaft 3.
Specifically, the pump body assembly comprises a main bearing 4 and a secondary bearing 5, wherein the main bearing 4 and the secondary bearing 5 are correspondingly arranged at two opposite ends of the cylinder 1 so as to support the crankshaft 3 through the main bearing 4 and the secondary bearing 5; the main bearing 4 is positioned on one side of the auxiliary bearing 5 close to the power input end of the crankshaft 3; when the roller structure 2 is composed of the first roller 21 and the second roller 22, the displacement V of the pump body assembly and the bearing area S of the main bearing 43Ratio of (V/S)3Is in the range of 37 to 44; displacement V of pump body assembly and bearing area S of auxiliary bearing 54Ratio of (V/S)4Ranges from 76 to 88; wherein the bearing area S of the main bearing 43The area of the orthographic projection of the contact surface of the main bearing 4 and the crankshaft 3 in a fourth plane is vertical to the direction of the pressure applied to the crankshaft 3 by the main bearing 4; bearing surface S of the secondary bearing 54The area of the orthogonal projection of the contact surface of the sub-bearing 5 and the crankshaft 3 in the fifth plane is perpendicular to the direction of the pressure applied by the sub-bearing 5 to the crankshaft 3.
Likewise, internal friction losses of the pump block assembly also exist between the crankshaft 3 and the main bearing 4, and between the crankshaft 3 and the auxiliary bearing 5. At present, in the design process of the compressor, the bearing area (effective stress area) between the crankshaft 3 and the main bearing 4 is usually designed to be as large as possible, so that the support stability of the crankshaft 3 and the lubrication effect between the crankshaft 3 and the main bearing 4 and the auxiliary bearing 5 can be improved. Therefore, the range of values mentioned above for the pump body assembly of the existing compressor is significantly smaller than that mentioned above in the present applicationEach value is taken. I.e. for a single-roller pump body assembly, the displacement V of the pump body assembly and in particular the bearing area S of the main bearing 46Ratio of (V/S)6Significantly less than 22, the displacement V of its pump body assembly and in particular the bearing area S of the secondary bearing 57Ratio of (V/S)7Significantly less than 48. For a pump body assembly of a double-roller structure, the displacement V of the pump body assembly and the bearing area S of the main bearing 4 in particular3Ratio of (V/S)3Significantly less than 37, the displacement V of its pump body assembly and in particular the bearing area S of the secondary bearing 54Ratio of (V/S)4Significantly less than 76.
In particular, the displacement V of the pump block assembly and the bearing area S of the main bearing 43Ratio of (V/S)3Is in the range of 37 to 41; displacement V of pump body assembly and bearing area S of auxiliary bearing 54Ratio of (V/S)4Is in the range of 76 to 80.
In particular, the displacement V of the pump block assembly and the bearing area S of the main bearing 43Ratio of (V/S)3Is in the range of 41 to 44; displacement V of pump body assembly and bearing area S of auxiliary bearing 54Ratio of (V/S)4Is in the range of 80 to 88.
Specifically, the contact surface of the main bearing 4 and the crankshaft 3 is a third cylindrical surface, and the contact surface of the auxiliary bearing 5 and the crankshaft 3 is a fourth cylindrical surface; the diameter of the third cylindrical surface is d3The height of the third cylindrical surface is h3The diameter of the fourth cylindrical surface is d4The height of the fourth cylindrical surface is h4(ii) a Bearing area S of the main bearing 43＝d3×h3Bearing surface area S of the secondary bearing 54＝d4×h4。
It should be noted that the displacement V of the pump body assembly corresponds to the unit of each bearing area, that is, if the unit of the displacement V is cm3The unit of each bearing area is cm2(ii) a If the unit of the discharge volume V is mm3The unit of each bearing area is mm2。
As shown in fig. 5, there is provided a rotary compressor including: the pump body assembly 100, the pump body assembly 100 is the pump body assembly; the motor assembly 200 is used for driving the crankshaft 3 of the pump body assembly 100 to rotate; a liquid separator 300 for separating the gaseous refrigerant from the liquid refrigerant; the liquid separator 300 is connected to an intake port of the cylinder 1 of the pump block assembly 100 to supply gaseous refrigerant to the cylinder 1.
In addition, the invention further provides an air conditioner, and particularly the air conditioner comprises the rotor compressor.
From the above description, it can be seen that the above-described embodiments of the present invention achieve the following technical effects:
the pump body assembly comprises a cylinder 1, a roller structure 2 and a crankshaft 3, wherein the roller structure 2 is arranged in a compression cavity of the cylinder 1, and the roller structure 2 is sleeved on the crankshaft 3 so as to drive the roller structure 2 to roll along the inner wall of the compression cavity through the crankshaft 3; when the roller structure 2 is a roller, the displacement V of the pump body assembly and the bearing area S of the roller5Ratio of (V/S)5Is in the range of 29 to 36; when the roller structure 2 is composed of two rollers, which are a first roller 21 and a second roller 22, respectively, the first roller 21 is located on one side of the second roller 22 close to the power input end of the crankshaft 3; the displacement V of the pump body assembly and the bearing area S of the first roller 211Ratio of (V/S)1The value range of (1) is 56 to 63; the displacement V of the pump body assembly and the bearing area S of the second roller 222Ratio of (V/S)2The value range of (a) is 60 to 70; the displacement V of the pump body assembly is the displacement of the pump body assembly in one working cycle; bearing area S of roller5The area of the orthographic projection of the contact surface of the roller and the crankshaft 3 in a first plane is vertical to the direction of the pressure applied to the roller by the crankshaft 3; bearing area S of first roller 211Is the orthographic projection area of the contact surface of the first roller 21 and the crankshaft 3 in a second plane, and the second plane is vertical to the direction of the pressure applied to the first roller 21 by the crankshaft 3; bearing area S of the second roller 222The area of the orthogonal projection of the contact surface of the second drum 22 and the crankshaft 3 in the third plane is perpendicular to the direction of the pressure applied by the crankshaft 3 to the second drum 22. By designing the bearing area (effective bearing area) of the contact surface of the roller structure 2 and the crankshaft 3, the bearing area is designedPump body assembly of single-roller construction, with displacement V of the pump body assembly and bearing area S of the roller in particular5Ratio of (V/S)5Is in the range of 29 to 36; aiming at the pump body component with a double-roller structure, the discharge volume V of the pump body component and the bearing area S of the first roller 21 are enabled1Ratio of (V/S)1The value range of (1) is 56 to 63; in particular the displacement V of the pump body assembly and in particular the bearing area S of the second roller 222Ratio of (V/S)2Is in the range of 60 to 70. Through the arrangement, the area of the contact surface of the crankshaft 3 and the roller structure 2 is in a better range, an oil film with proper thickness can be formed between the crankshaft and the roller structure, the lubricating effect is improved, the friction power loss of the pump body assembly is reduced, and the energy efficiency of the rotor compressor is improved.
Spatially relative terms, such as "above … …," "above … …," "above … …," "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 of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in the figures is turned over, devices described as "above" or "on" other devices or configurations would then be oriented "below" or "under" the other devices or configurations. Thus, the exemplary term "above … …" can include both an orientation of "above … …" and "below … …". The device may be otherwise variously oriented (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 example embodiments according to the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise.
It should be noted that the terms "first," "second," and the like in the description and claims of this application and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used is interchangeable under appropriate circumstances such that the embodiments of the application described herein are, for example, capable of operation in sequences other than those illustrated or otherwise described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed, but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (11)

1. A pump body assembly comprises a cylinder (1), a roller structure (2) and a crankshaft (3), wherein the roller structure (2) is installed in a compression cavity of the cylinder (1), and the crankshaft (3) is sleeved with the roller structure (2) so as to drive the roller structure (2) to roll along the inner wall of the compression cavity through the crankshaft (3); it is characterized in that the preparation method is characterized in that,
when the roller structure (2) is a roller, the displacement V of the pump body assembly and the bearing area S of the roller5Ratio of (V/S)5Is in the range of 29 to 36;
when the roller structure (2) consists of two rollers, the two rollers are respectively a first roller (21) and a second roller (22), and the first roller (21) is positioned on one side of the second roller (22) close to the power input end of the crankshaft (3); of said pump body assemblyThe volume V and the bearing area S of the first roller (21)1Ratio of (V/S)1The value range of (1) is 56 to 63; the displacement volume V of the pump body assembly and the bearing area S of the second roller (22)2Ratio of (V/S)2The value range of (a) is 60 to 70;
the displacement V of the pump body assembly is the displacement of the pump body assembly in one working cycle; bearing area S of the roller5Is the orthographic projection area of the contact surface of the roller and the crankshaft (3) in a first plane, and the first plane is vertical to the direction of the pressure applied to the roller by the crankshaft (3); the bearing area S of the first roller (21)1Is the orthographic projection area of the contact surface of the first roller (21) and the crankshaft (3) in a second plane, and the second plane is vertical to the direction of the pressure applied to the first roller (21) by the crankshaft (3); the bearing area S of the second roller (22)2Is the orthographic projection area of the contact surface of the second roller (22) and the crankshaft (3) in a third plane, and the third plane is perpendicular to the direction of the pressure applied to the second roller (22) by the crankshaft (3).
2. The pump body assembly of claim 1,
when the roller structure (2) is a roller, the contact surface of the roller and the crankshaft (3) is a cylindrical surface, and the diameter of the cylindrical surface is d5The height of the cylindrical surface is h5(ii) a Bearing area S of the roller5＝d5×h5；
When the roller structure (2) consists of two rollers, the contact surface of the first roller (21) and the crankshaft (3) is a first cylindrical surface, and the contact surface of the second roller (22) and the crankshaft (3) is a second cylindrical surface; the diameter of the first cylindrical surface is d1The height of the first cylindrical surface is h1The diameter of the second cylindrical surface is d2The height of the second cylindrical surface is h2(ii) a The bearing area S of the first roller (21)1＝d1×h1Bearing surface of the second roller (22)Product S2＝d2×h2。
3. Pump body assembly according to claim 1, characterized in that the displacement volume V of the pump body assembly and the bearing area S of the first roller (21) when the roller structure (2) consists of two rollers1Ratio of (V/S)1Is in the range of 56 to 60; the displacement volume V of the pump body assembly and the bearing area S of the second roller (22)2Ratio of (V/S)2Is in the range of 60 to 66.
4. Pump body assembly according to claim 1, characterized in that the displacement volume V of the pump body assembly and the bearing area S of the first roller (21) when the roller structure (2) consists of two rollers1Ratio of (V/S)1The value range of (a) is 60 to 63; the displacement volume V of the pump body assembly and the bearing area S of the second roller (22)2Ratio of (V/S)2Is in the range of 66 to 70.
5. The pump body assembly according to claim 1, characterized in that it comprises a main bearing (4) and a secondary bearing (5), said main bearing (4) and said secondary bearing (5) being provided at opposite ends of said cylinder (1) respectively, to support said crankshaft (3) through said main bearing (4) and said secondary bearing (5); the main bearing (4) is positioned on one side of the auxiliary bearing (5) close to the power input end of the crankshaft (3); when the roller structure (2) is a roller, the displacement V of the pump body assembly and the bearing area S of the main bearing (4)6Ratio of (V/S)6Is in the range of 22 to 27; the discharge volume V of the pump body assembly and the bearing area S of the auxiliary bearing (5)7Ratio of (V/S)7Is in the range of 48 to 57;
wherein the bearing area S of the main bearing (4)6The area of the orthographic projection of the contact surface of the main bearing (4) and the crankshaft (3) in a fourth plane is perpendicular to the direction of the pressure applied to the crankshaft (3) by the main bearing (4); the auxiliary bearing (5)Bearing area S7The area of the orthographic projection of the contact surface of the auxiliary bearing (5) and the crankshaft (3) in a fifth plane is perpendicular to the direction of the pressure applied to the crankshaft (3) by the auxiliary bearing (5).
6. The pump body assembly according to claim 1, characterized in that it comprises a main bearing (4) and a secondary bearing (5), said main bearing (4) and said secondary bearing (5) being provided at opposite ends of said cylinder (1) respectively, to support said crankshaft (3) through said main bearing (4) and said secondary bearing (5); the main bearing (4) is positioned on one side of the auxiliary bearing (5) close to the power input end of the crankshaft (3); when the roller structure (2) is composed of the first roller (21) and the second roller (22), the displacement volume V of the pump body assembly and the bearing area S of the main bearing (4)3Ratio of (V/S)3Is in the range of 37 to 44; the discharge volume V of the pump body assembly and the bearing area S of the auxiliary bearing (5)4Ratio of (V/S)4Ranges from 76 to 88;
wherein the bearing area S of the main bearing (4)3The area of the orthographic projection of the contact surface of the main bearing (4) and the crankshaft (3) in a fourth plane is perpendicular to the direction of the pressure applied to the crankshaft (3) by the main bearing (4); the bearing area S of the secondary bearing (5)4The area of the orthographic projection of the contact surface of the auxiliary bearing (5) and the crankshaft (3) in a fifth plane is perpendicular to the direction of the pressure applied to the crankshaft (3) by the auxiliary bearing (5).
7. Pump body assembly according to claim 6, characterized in that the displacement volume V of the pump body assembly and the bearing area S of the main bearing (4)3Ratio of (V/S)3Is in the range of 37 to 41; the discharge volume V of the pump body assembly and the bearing area S of the auxiliary bearing (5)4Ratio of (V/S)4Is in the range of 76 to 80.
8. The method of claim 6The pump body assembly is characterized in that the displacement V of the pump body assembly and the bearing area S of the main bearing (4)3Ratio of (V/S)3Is in the range of 41 to 44; the discharge volume V of the pump body assembly and the bearing area S of the auxiliary bearing (5)4Ratio of (V/S)4Is in the range of 80 to 88.
9. The pump block assembly according to claim 6, characterized in that the contact surface of the main bearing (4) with the crankshaft (3) is a third cylindrical surface and the contact surface of the secondary bearing (5) with the crankshaft (3) is a fourth cylindrical surface; the diameter of the third cylindrical surface is d3The height of the third cylindrical surface is h3The diameter of the fourth cylindrical surface is d4The height of the fourth cylindrical surface is h4(ii) a The bearing area S of the main bearing (4)3＝d3×h3The bearing area S of the secondary bearing (5)4＝d4×h4。
10. A rotary compressor, characterized in that the rotary compressor comprises:
a pump body assembly (100), the pump body assembly (100) being the pump body assembly of any one of claims 1 to 9;
a motor assembly (200), wherein the motor assembly (200) is used for driving a crankshaft (3) of the pump body assembly (100) to rotate;
a liquid separator (300) for separating gaseous refrigerant from liquid refrigerant; the liquid separator (300) is connected to a suction port of a cylinder (1) of the pump body assembly (100) to supply gaseous refrigerant to the cylinder (1).
11. An air conditioner characterized in that it comprises the rotary compressor of claim 10.
CN202011401662.1A 2020-12-03 2020-12-03 Pump body subassembly, rotor compressor and air conditioner Pending CN112460021A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202011401662.1A CN112460021A (en) 2020-12-03 2020-12-03 Pump body subassembly, rotor compressor and air conditioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202011401662.1A CN112460021A (en) 2020-12-03 2020-12-03 Pump body subassembly, rotor compressor and air conditioner

Publications (1)

Publication Number Publication Date
CN112460021A true CN112460021A (en) 2021-03-09

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202011401662.1A Pending CN112460021A (en) 2020-12-03 2020-12-03 Pump body subassembly, rotor compressor and air conditioner

Country Status (1)

Country Link
CN (1) CN112460021A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114263611A (en) * 2021-12-30 2022-04-01 安徽美芝精密制造有限公司 Compressor and air conditioner

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114263611A (en) * 2021-12-30 2022-04-01 安徽美芝精密制造有限公司 Compressor and air conditioner
CN114263611B (en) * 2021-12-30 2024-03-01 安徽美芝精密制造有限公司 Compressor and air conditioner

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