CN112460017A - Pump body assembly and fluid machine with same - Google Patents

Pump body assembly and fluid machine with same Download PDF

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Publication number
CN112460017A
CN112460017A CN202011396227.4A CN202011396227A CN112460017A CN 112460017 A CN112460017 A CN 112460017A CN 202011396227 A CN202011396227 A CN 202011396227A CN 112460017 A CN112460017 A CN 112460017A
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CN
China
Prior art keywords
cylinder
pump body
roller
body assembly
shaft section
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
CN202011396227.4A
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Chinese (zh)
Inventor
巩庆霞
柯达俊
罗惠芳
吴健
邓罡
尹雪峰
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 CN202011396227.4A priority Critical patent/CN112460017A/en
Publication of CN112460017A publication Critical patent/CN112460017A/en
Priority to PCT/CN2021/110071 priority patent/WO2022116577A1/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
    • 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
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C2240/60—Shafts

Abstract

The invention provides a pump body assembly and a fluid machine with the same. Wherein, pump body subassembly includes: the air cylinder assembly comprises an air cylinder, a roller and a sliding sheet, wherein the air cylinder is provided with an inner cavity and a sliding sheet groove communicated with the inner cavity, the roller is rotatably arranged in the inner cavity, the sliding sheet is slidably arranged in the sliding sheet groove, and the head of the sliding sheet is in contact with the peripheral surface of the roller; the crankshaft is arranged on the cylinder assembly in a penetrating mode and comprises an eccentric part, the eccentric part is located in the inner cavity, and the roller is sleeved on the eccentric part; wherein, the eccentricity e of the eccentric part and the inner circle radius R of the cylinder satisfy the following relationship:
Figure DDA0002815363630000011
or
Figure DDA0002815363630000012
Or
Figure DDA0002815363630000013
The invention effectively solves the problem that the optimal relative eccentricity is not selected in the prior art.

Description

Pump body assembly and fluid machine with same
Technical Field
The invention relates to the technical field of pump body assemblies, in particular to a pump body assembly and a fluid machine with the same.
Background
At present, a single-rotor type rolling rotor compressor is widely applied to the field of household air conditioners, and efficiency improvement and cost reduction are two major development trends and targets of the rolling rotor compressor. In particular, the miniaturization of the compressor is an important way to reduce the cost, and the improvement needs to be based on the structure of the compressor. The relative eccentricity phi (i.e. the ratio of the eccentric amount e of the crankshaft to the radius R of the inner circle of the cylinder) is crucial to the performance of the compressor.
However, in the prior art, from the viewpoint of improving the utilization rate of the cylinder volume, reducing the volume and weight of the compressor and improving the performance of the compressor, a relatively large value of the eccentricity Φ is preferably selected, but as the eccentricity e increases, the difficulty of the compressor in structural design increases, and meanwhile, the contact force and the friction wear between the sliding vane and the roller increase, which causes the power consumption of the compressor to increase and the reliability to decrease. Therefore, the prior art does not have the optimal relative eccentricity Φ to make the compressor performance in a superior state.
Disclosure of Invention
The invention mainly aims to provide a pump body assembly and a fluid machine with the same, so as to solve the problem that the optimal relative eccentricity is not selected in the prior art.
In order to achieve the above object, according to one aspect of the present invention, there is provided a pump body assembly including: the cylinder assembly comprises a cylinder, a roller and a sliding sheet, wherein the cylinder is provided with an inner cavity and a sliding sheet groove communicated with the inner cavity, the roller is rotatably arranged in the inner cavity, and the sliding sheet is slidably arranged in the sliding sheet grooveAnd the head of the sliding sheet is contacted with the peripheral surface of the roller; the crankshaft is arranged on the cylinder assembly in a penetrating mode and comprises an eccentric part, the eccentric part is located in the inner cavity, and the roller is sleeved on the eccentric part; wherein, the eccentricity e of the eccentric part and the inner circle radius R of the cylinder satisfy the following relationship:
Figure BDA0002815363610000011
or
Figure BDA0002815363610000012
Or
Figure BDA0002815363610000013
Further, the height H of the cylinder and the inner circle diameter D of the cylinder satisfy the following relationship:
Figure BDA0002815363610000014
further, the height H of the cylinder and the inner circle diameter D of the cylinder satisfy the following relationship:
Figure BDA0002815363610000015
further, the height H of the cylinder and the inner circle diameter D of the cylinder satisfy the following relationship:
Figure BDA0002815363610000016
furthermore, the crankshaft also comprises a long shaft section and a short shaft section, the long shaft section and the short shaft section are connected through an eccentric part, and the outer diameters of the long shaft section and the short shaft section are consistent; wherein, the following relation is satisfied between the displacement V of pump body subassembly and the external diameter d of long shaft section:
Figure BDA0002815363610000021
further, the air displacement V of the pump body assembly and the outer diameter d of the long shaft section satisfy the following relation:
Figure BDA0002815363610000022
further, the air displacement V of the pump body assembly and the outer diameter d of the long shaft section satisfy the following relation:
Figure BDA0002815363610000023
further, the thickness a of the roller satisfies the following relationship: a is more than or equal to 3.80 and less than or equal to 7.85.
Further, the thickness a of the roller satisfies the following relationship: a is more than or equal to 3.80 and less than or equal to 7.5.
Further, the cylinder assemblies are two, the two cylinder assemblies are arranged at intervals along the height direction of the pump body assembly, the crankshaft comprises two eccentric parts, and the two eccentric parts are arranged in one-to-one correspondence with the rollers of the two cylinder assemblies.
According to another aspect of the present invention, there is provided a fluid machine including the pump body assembly described above.
By applying the technical scheme of the invention, in the operation process of the pump body assembly, the driving device drives the crankshaft to rotate, so that the roller sleeved outside the eccentric part of the crankshaft moves in the cylinder, and further the refrigerant is compressed and discharged. Like this, the above-mentioned relation between the eccentric value e of eccentric portion and the interior circle radius R of cylinder makes relative eccentricity (the ratio of eccentric value e and the interior circle radius R of cylinder) be the optimum value, and then has improved cylinder volume utilization ratio, has reduced the volume that occupies of pump body subassembly, has promoted the operating property of pump body subassembly, has reduced the consumption of pump body subassembly, solves among the prior art and does not carry out the problem of choosing to optimum relative eccentricity, has promoted the operational reliability of pump body subassembly.
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 front view of an embodiment of a pump body assembly according to the present invention;
FIG. 2 shows an enlarged schematic view at A of the pump body assembly of FIG. 1;
fig. 3 shows a sectional view of an embodiment of a fluid machine according to the invention;
FIG. 4 shows a diagram of the relationship between the relative eccentricity Φ of the fluid machine and the coefficient of performance COP of the compressor;
fig. 5 shows a diagram of the relationship between the aspect ratio λ and the coefficient of performance COP of the compressor of a fluid machine;
FIG. 6 is a graph showing the relationship between the ratio ε of the displacement V to the shaft diameter of the fluid machine and the coefficient of performance COP of the compressor; and
fig. 7 shows a graph of the relationship between the thickness a of the roller of the turbomachine and the coefficient of performance COP of the compressor.
Wherein the figures include the following reference numerals:
10. a cylinder; 11. an inner cavity; 12. a slide groove; 20. a roller; 30. sliding blades; 40. a crankshaft; 41. an eccentric portion; 42. a long shaft section; 43. a short shaft section; 50. an upper cover assembly; 60. a housing assembly; 70. a lower cover assembly; 80. a drive device; 81. a stator; 82. a rotor; 90. a liquid separator; 100. an upper flange; 110. a lower flange; 120. a lower cover plate; 130. a spring; 140. a separator.
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.
It is noted that, unless otherwise indicated, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs.
In the present invention, unless stated to the contrary, use of the directional terms "upper and lower" are generally directed to the orientation shown in the drawings, or to the vertical, or gravitational direction; likewise, for ease of understanding and description, "left and right" are generally to the left and right as shown in the drawings; "inner and outer" refer to the inner and outer relative to the profile of the respective member itself, but the above directional terms are not intended to limit the present invention.
In order to solve the problem that the optimal relative eccentricity is not selected in the prior art, the application provides a pump body assembly and a fluid machine with the same.
As shown in fig. 1 and 3, the pump body assembly includes a cylinder assembly and a crankshaft 40. The cylinder assembly comprises a cylinder 10, a roller 20 and a sliding sheet 30, wherein the cylinder 10 is provided with an inner cavity 11 and a sliding sheet groove 12 communicated with the inner cavity 11, the roller 20 is rotatably arranged in the inner cavity 11, the sliding sheet 30 is slidably arranged in the sliding sheet groove 12, and the head of the sliding sheet 30 is in contact with the outer peripheral surface of the roller 20. The crankshaft 40 is disposed on the cylinder assembly in a penetrating manner, the crankshaft 40 includes an eccentric portion 41, the eccentric portion 41 is located in the inner cavity 11, and the roller 20 is disposed on the eccentric portion 41. Wherein, the eccentricity e of the eccentric part 41 and the inner circle radius R of the cylinder 10 satisfy the following relationship:
Figure BDA0002815363610000031
by applying the technical scheme of the embodiment, in the operation process of the pump body assembly, the driving device drives the crankshaft 40 to rotate, so that the roller 20 sleeved outside the eccentric portion 41 of the crankshaft 40 moves in the cylinder 10, and further compresses and discharges the refrigerant. Like this, the above-mentioned relation between the eccentric volume e of eccentric portion 41 and the interior circle radius R of cylinder 10 makes relative eccentricity (the ratio of eccentric volume e and the interior circle radius R of cylinder) be the optimum value, and then has improved cylinder volume utilization, has reduced the volume that occupies of pump body subassembly, has promoted the operating property of pump body subassembly, has reduced the consumption of pump body subassembly, solves the problem that does not select optimum relative eccentricity among the prior art, has promoted the operating reliability of pump body subassembly.
Note that the relationship between the eccentric amount e of the eccentric portion 41 and the inner circle radius R of the cylinder 10 is not limited to this. In other embodiments not shown in the drawings, the eccentricity e of the eccentric portion and the inner circle radius R of the cylinder satisfy the following relationship:
Figure BDA0002815363610000032
thus, the above-mentioned relationship between the eccentric amount e of the eccentric portion and the inner circle radius R of the cylinder 10 makes the relative eccentricity (the ratio of the eccentric amount e to the inner circle radius R of the cylinder) an optimum value, and furtherThe cylinder volume utilization rate is improved, the occupied volume of the pump body assembly is reduced, the operation performance of the pump body assembly is improved, the power consumption of the pump body assembly is reduced, the problem that the optimal relative eccentricity is not selected in the prior art is solved, and the operation reliability of the pump body assembly is improved.
Note that the relationship between the eccentric amount e of the eccentric portion 41 and the inner circle radius R of the cylinder 10 is not limited to this. In other embodiments not shown in the drawings, the eccentricity e of the eccentric portion and the inner circle radius R of the cylinder satisfy the following relationship:
Figure BDA0002815363610000041
like this, the above-mentioned relation between the eccentric value e of eccentric portion and the interior circle radius R of cylinder 10 makes relative eccentricity (the ratio of eccentric value e and the interior circle radius R of cylinder) be the optimum value, and then has improved cylinder volume utilization ratio, has reduced the volume that occupies of pump body subassembly, has promoted the operating property of pump body subassembly, has reduced the consumption of pump body subassembly, solves among the prior art and does not carry out the problem of choosing to optimum relative eccentricity, has promoted the operational reliability of pump body subassembly.
In the present embodiment, the relative eccentricity Φ (the ratio of the eccentric amount e of the eccentric portion 41 to the inner circle radius R of the cylinder 10) has a large influence on the structural size of the pump body assembly and the utilization rate of the cylinder volume, which is the utilization rate of the cylinder volume
Figure BDA0002815363610000042
From the perspective of improving the volume utilization rate of the cylinder, reducing the volume and weight of the pump body assembly (compressor) and improving the performance of the pump body assembly (compressor), phi is suitable to select a larger value, but along with the increase of the eccentric amount e, the difficulty of the pump body assembly (compressor) in structural design is increased, meanwhile, the contact force and the friction loss between the sliding sheet 30 and the roller 20 are increased, and the power consumption and the reliability of the pump body assembly (compressor) are increased and reduced.
Alternatively, the height H of the cylinder 10 and the inner circle diameter D of the cylinder 10 satisfy the following relationship:
Figure BDA0002815363610000043
specifically, the influence of the ratio of the height H of the cylinder 10 to the inner circle diameter D of the cylinder 10 on the pump body assembly is mainly reflected in the change of the stress of the roller and the slide sheet and the change of the leakage amount of the compression cavity to the suction cavity. The smaller the ratio of the height H of the cylinder 10 to the inner circle diameter D of the cylinder 10, the shorter the height of the cylinder 10, the smaller the gas force applied to the side surfaces of the roller 20 and the vane 30, and the smaller the circumferential leakage of the gas through the contact point gap between the cylinder 10 and the roller 20 and the contact point gap between the vane 30 and the roller 20. However, an excessively small cylinder height not only results in an increase in the diameter of the cylinder 10, but also an increase in the overall size of the pump body assembly; it also results in increased sliding speed between the sliding vane 30 and the roller 20, increased wear, and a reduced service life of the pump body assembly. Thus, the above-described relationship between the height H of the cylinder 10 and the inner circle diameter D of the cylinder 10 allows the aspect ratio of the cylinder 10 to be set within an optimum range to place the pump body assembly in a superior condition in performance.
Alternatively, the height H of the cylinder 10 and the inner circle diameter D of the cylinder 10 satisfy the following relationship:
Figure BDA0002815363610000044
thus, the above-described relationship between the height H of the cylinder 10 and the inner circle diameter D of the cylinder 10 allows the aspect ratio of the cylinder 10 to be set within an optimum range to place the pump body assembly in a superior condition in performance.
Alternatively, the height H of the cylinder 10 and the inner circle diameter D of the cylinder 10 satisfy the following relationship:
Figure BDA0002815363610000045
thus, the above-described relationship between the height H of the cylinder 10 and the inner circle diameter D of the cylinder 10 allows the aspect ratio of the cylinder 10 to be set within an optimum range to place the pump body assembly in a superior condition in performance.
Optionally, the crankshaft 40 further includes a long shaft segment 42 and a short shaft segment 43, the long shaft segment 42 and the short shaft segment 43 are connected by the eccentric portion 41, and the outer diameters of the long shaft segment 42 and the short shaft segment 43 are identical. Wherein, the following relation is satisfied between the displacement V of the pump body assembly and the outer diameter d of the long shaft section 42:
Figure BDA0002815363610000051
specifically, the design of the ratio of the displacement V of the pump body assembly to the outer diameter d of the long shaft section 42 is crucial to the performance and reliability of the pump body assembly (compressor), and if the ratio of the displacement V of the pump body assembly to the outer diameter d of the long shaft section 42 is too large, the friction power consumption of the pump body assembly is increased, which is unfavorable to the performance; if the ratio of the displacement V of the pump body assembly to the outer diameter d of the long shaft section 42 is too small, the deflection of the crankshaft of the pump body assembly increases, and abnormal wear is likely to occur. Thus, the above-described relationship of the ratio of the displacement V of the pump block assembly to the outer diameter d of the long shaft section 42 allows the aspect ratio of the cylinder 10 to be set within an optimum range, so that the performance of the pump block assembly is in a superior state.
Alternatively, the following relationship is satisfied between the displacement V of the pump block assembly and the outer diameter d of the long shaft section 42:
Figure BDA0002815363610000052
thus, the above-described relationship of the ratio of the displacement V of the pump block assembly to the outer diameter d of the long shaft section 42 allows the aspect ratio of the cylinder 10 to be set within an optimum range, so that the performance of the pump block assembly is in a superior state.
Alternatively, the following relationship is satisfied between the displacement V of the pump block assembly and the outer diameter d of the long shaft section 42:
Figure BDA0002815363610000053
thus, the above-described relationship of the ratio of the displacement V of the pump block assembly to the outer diameter d of the long shaft section 42 allows the aspect ratio of the cylinder 10 to be set within an optimum range, so that the performance of the pump block assembly is in a superior state.
Optionally, the thickness a of the roller 20 satisfies the following relationship: a is more than or equal to 3.80 and less than or equal to 7.85. Specifically, the contact area between the roller 20 and the lower flange 110 or the partition plate 140 directly affects the end face leakage and the friction loss of the roller 20, and the larger the thickness a of the roller 20, the smaller the end face leakage, but the larger the corresponding end face friction loss. Therefore, it is important to select an appropriate roller thickness to balance the leakage loss and the friction loss. Thus, the above-described arrangement of the thickness a of the roller 20 allows a good balance between the leakage loss and the friction loss to be obtained, so that the performance of the pump block assembly is in a better state.
Optionally, the thickness a of the roller 20 satisfies the following relationship: a is more than or equal to 3.80 and less than or equal to 7.5. Thus, the above-described arrangement of the thickness a of the roller 20 allows a good balance between the leakage loss and the friction loss to be obtained, so that the performance of the pump block assembly is in a better state.
Alternatively, the number of the cylinder assemblies is two, the two cylinder assemblies are arranged at intervals along the height direction of the pump body assembly, the crankshaft 40 comprises two eccentric parts 41, and the two eccentric parts 41 are arranged in one-to-one correspondence with the rollers 20 of the two cylinder assemblies. Like this, above-mentioned setting makes the pump body subassembly be double-cylinder pump body subassembly, and then has promoted the operating efficiency of pump body subassembly.
As shown in fig. 1 to 3, the pump body assembly further includes an upper flange 100, a lower flange 110, a lower cover plate 120, and a spring 130. The spring 130 is disposed in the slide groove 12, one end of the spring 130 abuts against one end of the slide 30 away from the roller 20, and the other end of the spring 130 abuts against an inner wall of the slide groove 12, so as to apply an elastic force to the slide 30 moving toward the roller 20. The upper flange 100 is disposed above the cylinder 10 and has an exhaust hole, the lower flange 110 is disposed below the cylinder 10, and the lower cover plate 120 is disposed below the lower flange 110 and is connected to the lower flange 110.
As shown in fig. 3, the present application also provides a fluid machine including the pump body assembly described above. Optionally, the fluid machine is a compressor.
In the present embodiment, the compressor coefficient of performance COP satisfies the following relationship:
Figure BDA0002815363610000061
wherein, Q is the refrigerating capacity of the compressor, the size of the refrigerating capacity is influenced by leakage, and the leakage is influenced by the thickness a of the roller 20, the height H of the cylinder 10 and the inner circle diameter D of the cylinder 10. W is power consumption of the compressor, and the power consumption is related to friction loss, indication power loss, and the like, and the friction loss is related to the thickness a of the roller 20, the inner circle radius R of the cylinder 10, and the eccentric amount e of the eccentric portion 41. The relationship between the relative eccentricity Φ (the ratio of the eccentric amount e of the eccentric portion 41 to the inner circle radius R of the cylinder 10) and the compressor coefficient of performance COP is shown in fig. 4, and when the relative eccentricity Φ ranges from 0.17 to 0.25, the compressor coefficient of performance reaches the optimum range. The relationship between the height-diameter ratio lambda (the ratio of the height H of the cylinder 10 to the inner circle diameter D of the cylinder 10) and the coefficient of performance COP of the compressor is shown in fig. 5, the coefficient of performance of the compressor increases and then decreases as the height-diameter ratio lambda increases, and the coefficient of performance of the compressor reaches a better range when the range of the height-diameter ratio lambda is 0.4 to 0.58. The relationship between the ratio epsilon of the displacement V to the shaft diameter (the ratio of the displacement V of the pump body assembly to the outer diameter d of the long shaft section 42), the coefficient of performance COP of the compressor and the wear loss of parts is shown in FIG. 6, when the ratio of the displacement V to the shaft diameter of the crankshaft is in the range of 0.6 to epsilon of 1.8, the performance of the compressor reaches a better range, and the wear loss of the compressor is smaller at the moment. The relationship between the thickness a of the roller 20 and the coefficient of performance COP of the compressor is shown in fig. 7, and when the thickness of the roller 20 is in the range of 4-7.5 mm, the coefficient of performance of the compressor is measured to reach a better range.
As shown in fig. 3, the fluid machine further includes a top cover assembly 50, a housing assembly 60, a driving device 80, a dispenser 90, and a bottom cover assembly 70. The upper cover assembly 50 covers the housing assembly 60, the lower cover assembly 70 is located below the housing assembly 60 and connected to the housing assembly 60, the upper cover assembly 50, the housing assembly 60 and the lower cover assembly 70 form an installation cavity, and the driving device 80 and the pump body assembly are all disposed in the installation cavity. The driving device 80 includes a stator 81 and a rotor 82, and the driving device 80 is sleeved outside the long shaft section 42 of the crankshaft 40 and drives the long shaft section 42 to rotate, so as to drive the crankshaft 40 to rotate. The liquid distributor 90 is connected to both the exhaust and intake ports of the pump body assembly.
Specifically, during the operation of the compressor, the head of the sliding vane 30 is closely attached to the outer wall of the roller 20, and reciprocates along the sliding vane slot 12 along with the rotation of the roller 20, and the crescent-shaped working volume formed by the roller 20, the sliding vane 30 and the cylinder 10 is continuously changed, so that the processes of air suction, compression and air exhaust of the compressor are realized, and when the length of the sliding vane 30 extending out of the sliding vane slot 12 is long (when the eccentric amount e is large, the length of the sliding vane 30 extending out is long), the following performance between the roller 20 and the sliding vane 30 is poor, and the stability of the sliding vane 30 is also poor. In addition, the outer circumferential surface of the roller 20 is in clearance fit with the inner circumferential surface of the cylinder 10, end surface leakage (related to the thickness a of the roller 20) of the roller 20, the height direction of the slide 30 and the cylinder 10, and the side surface of the slide 30 and the slide groove 12, and the sliding vane is sealed by an oil film during the operation of the compressor, but leakage still exists, the ratio of radial clearance leakage between the outer circumferential surface of the roller 20 and the inner circumferential surface of the cylinder 10 is the largest, and the height H of the cylinder 10 determines the stroke of a radial clearance leakage channel.
From the above description, it can be seen that the above-described embodiments of the present invention achieve the following technical effects:
in the operation process of the pump body assembly, the driving device drives the crankshaft to rotate, so that the roller sleeved outside the eccentric part of the crankshaft moves in the cylinder, and further the refrigerant is compressed and discharged. Like this, the above-mentioned relation between the eccentric value e of eccentric portion and the interior circle radius R of cylinder makes relative eccentricity (the ratio of eccentric value e and the interior circle radius R of cylinder) be the optimum value, and then has improved cylinder volume utilization ratio, has reduced the volume that occupies of pump body subassembly, has promoted the operating property of pump body subassembly, has reduced the consumption of pump body subassembly, solves among the prior art and does not carry out the problem of choosing to optimum relative eccentricity, has promoted the operational reliability of pump body subassembly.
It is to be understood that the above-described embodiments are only a few, but not all, embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
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 is intended to include the plural unless the context clearly dictates otherwise, and it should be further understood that the terms "comprises" and/or "comprising," when used in this specification, specify the presence of 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 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 capable of operation in sequences other than those illustrated or described herein.
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, comprising:
the air cylinder assembly comprises an air cylinder (10), a roller (20) and a sliding sheet (30), wherein the air cylinder (10) is provided with an inner cavity (11) and a sliding sheet groove (12) communicated with the inner cavity (11), the roller (20) is rotatably arranged in the inner cavity (11), the sliding sheet (30) is slidably arranged in the sliding sheet groove (12), and the head part of the sliding sheet (30) is in contact with the outer peripheral surface of the roller (20);
the crankshaft (40) is arranged on the cylinder assembly in a penetrating mode, the crankshaft (40) comprises an eccentric part (41), the eccentric part (41) is located in the inner cavity (11), and the roller (20) is sleeved on the eccentric part (41);
wherein the eccentricity e of the eccentric part (41) and the inner circle radius R of the cylinder (10) satisfy the following relation:
Figure FDA0002815363600000011
or
Figure FDA0002815363600000012
Or
Figure FDA0002815363600000013
2. The pump block assembly according to claim 1, characterized in that the height H of the cylinder (10) and the inner circle diameter D of the cylinder (10) satisfy the following relationship:
Figure FDA0002815363600000014
3. the pump block assembly according to claim 1, characterized in that the height H of the cylinder (10) and the inner circle diameter D of the cylinder (10) satisfy the following relationship:
Figure FDA0002815363600000015
4. the pump block assembly according to claim 1, characterized in that the height H of the cylinder (10) and the inner circle diameter D of the cylinder (10) satisfy the following relationship:
Figure FDA0002815363600000016
5. the pump body assembly according to claim 1, wherein the crankshaft (40) further comprises a long shaft section (42) and a short shaft section (43), the long shaft section (42) and the short shaft section (43) being connected by the eccentric portion (41), the long shaft section (42) and the short shaft section (43) having the same outer diameter; wherein the displacement V of the pump body assembly and the outer diameter d of the long shaft section (42) satisfy the following relation:
Figure FDA0002815363600000017
6. the pump block assembly according to claim 5, characterized in that the following relationship is satisfied between the displacement V of the pump block assembly and the outer diameter d of the long shaft section (42):
Figure FDA0002815363600000018
7. the pump block assembly according to claim 5, characterized in that the following relationship is satisfied between the displacement V of the pump block assembly and the outer diameter d of the long shaft section (42):
Figure FDA0002815363600000019
8. the pump body assembly according to claim 1, characterized in that the thickness a of the roller (20) satisfies the following relationship: a is more than or equal to 3.80 and less than or equal to 7.85.
9. The pump body assembly according to claim 1, characterized in that the thickness a of the roller (20) satisfies the following relationship: a is more than or equal to 3.80 and less than or equal to 7.5.
10. The pump body assembly according to claim 1, wherein the number of the cylinder assemblies is two, the two cylinder assemblies are arranged at intervals in a height direction of the pump body assembly, the crankshaft (40) includes two eccentric portions (41), and the two eccentric portions (41) are arranged in one-to-one correspondence with the rollers (20) of the two cylinder assemblies.
11. A fluid machine, characterized by comprising a pump body assembly according to any one of claims 1 to 10.
CN202011396227.4A 2020-12-03 2020-12-03 Pump body assembly and fluid machine with same Pending CN112460017A (en)

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WO2022116577A1 (en) * 2020-12-03 2022-06-09 珠海格力节能环保制冷技术研究中心有限公司 Pump body assembly and fluid machinery having same

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WO2022116577A1 (en) * 2020-12-03 2022-06-09 珠海格力节能环保制冷技术研究中心有限公司 Pump body assembly and fluid machinery having same
CN114370399A (en) * 2021-12-09 2022-04-19 珠海格力电器股份有限公司 Pump body subassembly and doublestage compressor
CN114370399B (en) * 2021-12-09 2023-01-17 珠海格力电器股份有限公司 Pump body subassembly and doublestage compressor

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