CN115434890A - Crankshaft assembly, variable frequency compressor and refrigeration equipment - Google Patents

Crankshaft assembly, variable frequency compressor and refrigeration equipment Download PDF

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Publication number
CN115434890A
CN115434890A CN202110608285.7A CN202110608285A CN115434890A CN 115434890 A CN115434890 A CN 115434890A CN 202110608285 A CN202110608285 A CN 202110608285A CN 115434890 A CN115434890 A CN 115434890A
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CN
China
Prior art keywords
connecting rod
oil
eccentric shaft
oil groove
groove
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Pending
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CN202110608285.7A
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Chinese (zh)
Inventor
徐超
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Anhui Meizhi Compressor Co Ltd
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Anhui Meizhi Compressor Co Ltd
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Application filed by Anhui Meizhi Compressor Co Ltd filed Critical Anhui Meizhi Compressor Co Ltd
Priority to CN202110608285.7A priority Critical patent/CN115434890A/en
Publication of CN115434890A publication Critical patent/CN115434890A/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/22—Compensation of inertia forces
    • F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
    • F16F15/264—Rotating balancer shafts
    • F16F15/267—Rotating balancer shafts characterised by bearing support of balancer shafts; Lubrication arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N1/00—Constructional modifications of parts of machines or apparatus for the purpose of lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/04—Lubrication

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Compressor (AREA)

Abstract

The invention belongs to the technical field of compressors, and particularly relates to a crankshaft assembly, a variable frequency compressor and refrigeration equipment. The bent axle subassembly includes bent axle and connecting rod, the bent axle includes the main shaft, balancing piece and eccentric shaft, the eccentric shaft is installed in the one end of main shaft, the main shaft is equipped with the main shaft oil groove, the eccentric shaft is equipped with the pump oil passageway that communicates with the main shaft oil groove, the tip of eccentric shaft is link up in the export of pump oil passageway, the connecting rod is including cup jointing the connecting rod link in the eccentric shaft, the lateral wall of eccentric shaft is equipped with the draining hole that communicates the pump oil passageway, the connecting rod link be equipped with the connecting rod oil groove of the clearance intercommunication between eccentric shaft and the balancing piece, when the eccentric shaft is rotatory, the draining hole can communicate or stagger with the connecting rod oil groove. When the oil drain hole and the balance block are communicated, lubricating oil can flow out through the oil drain hole, the connecting rod oil groove and a gap between the connecting rod connecting end and the balance block, and cannot enter the cylinder hole, so that the lubricating oil pumped to the cylinder hole in the whole operation period can be reduced, and excessive pump oil is avoided under the high-speed operation working condition.

Description

Crankshaft assembly, variable frequency compressor and refrigeration equipment
Technical Field
The invention belongs to the technical field of compressors, and particularly relates to a crankshaft assembly, a variable frequency compressor and refrigeration equipment.
Background
The variable frequency compressor is a compressor which can continuously change output energy by continuously adjusting the rotating speed of the variable frequency compressor within a certain range in a certain control mode or means, and compared with a constant rotating speed compressor, the variable frequency compressor can stably operate under the working conditions of low rotating speed and low energy consumption, has the advantages of high working efficiency, stable operation and low energy consumption, and is widely applied to electric appliances such as refrigerators, air conditioners and the like.
Generally, a lubricating oil supply system is required for the compressor, and the lubricating oil supply system is used for guiding lubricating oil to flow into or flow out of a crankshaft, so that each friction pair of the compressor is lubricated, and flexible operation of movable parts such as the crankshaft is ensured. In the case of the inverter compressor, a lubricating oil supply system thereof needs to satisfy lubricating oil supply in both low-frequency and high-frequency operation states, and in recent years, the development of the compressor tends to lower the frequency. However, for such an inverter compressor, due to the high oiling capability of the lubricating oil supply system, when the compressor is operated at a high frequency and a high rotation speed, the lubricating oil supply system may pump oil excessively, so that the lubricating oil of the compressor is supplied excessively at a high frequency, the oil output of the compressor is increased, and the inlet efficiency of the compressor (the ratio of the theoretical required input power to the actual input power of the compressor is referred to as inlet efficiency) is increased, so that the lubricating oil supply system may pump oil discontinuously, and the lubricating effect is affected.
Disclosure of Invention
The embodiment of the invention mainly aims to provide a crankshaft assembly, a variable frequency compressor and refrigeration equipment, and aims to solve the technical problems that in the prior art, a lubricating oil supply system of the variable frequency compressor is easy to pump excessive oil under a high-frequency working condition, so that the input efficiency of the compressor is increased, the oil pumping of the lubricating oil supply system is discontinuous, and the lubricating effect is influenced.
In order to achieve the above object, a lubricating oil supply system is required to be provided based on the compressor, and meanwhile, since the inverter compressor has two operating conditions of high frequency and low frequency, the oil pumping capacity of the lubricating oil supply system needs to be improved in order to meet the sufficient supply of the lubricating oil under the low frequency condition, and in the high frequency condition, in order to avoid excessive oil pumping, the high frequency oil supply capacity of the lubricating oil supply system needs to be reduced, so that the oil pumping capacity of the compressor is always kept in a relatively moderate range during high frequency operation. Based on the above, the inventor researches the oiling amount of the lubricating oil under the high-frequency working condition, designs various lubricating oil supply systems capable of stably supplying the lubricating oil under the high-frequency working condition, respectively tests each system, and provides the following technical scheme based on the test result.
The technical scheme adopted by the invention is as follows: the utility model provides a crankshaft assembly, including bent axle and connecting rod, the bent axle includes the main shaft, balancing piece and eccentric shaft, the eccentric shaft passes through balancing piece eccentric mounting in the one end of main shaft, the main shaft is provided with the main shaft oil groove, be provided with the pump oil passageway that extends to the main shaft and communicate with the main shaft oil groove in the eccentric shaft, the export of pump oil passageway extends to the tip that link up the eccentric shaft and deviate from the main shaft, the connecting rod is including cup jointing the connecting rod link in the eccentric shaft, the lateral wall of eccentric shaft is provided with the draining hole that communicates the pump oil passageway, the inside wall of connecting rod link is provided with the connecting rod oil groove, the clearance has between connecting rod link and the balancing piece, connecting rod oil groove and this clearance intercommunication, when the relative connecting rod link of eccentric shaft rotates, the draining hole can rotate to communicate or stagger with the connecting rod oil groove.
In some embodiments, the oil drain hole is arranged at the lower end part of the eccentric shaft facing the balance block and is positioned at the side part of the eccentric shaft far away from the central line of the main shaft, and the connecting rod oil groove is arranged at the lower end part of the connecting rod connecting end facing the balance block.
In some embodiments, the connecting rod further includes a connecting rod driving end disposed opposite to the connecting rod connecting end, and a rod body having two ends respectively connected to the connecting rod connecting end and the connecting rod driving end, and the connecting rod oil groove is disposed on a side of the connecting rod connecting end away from the connecting rod driving end.
In some embodiments, the connecting rod oil groove is a notch arranged on the inner side wall of the connecting rod connecting end and faces the bottom of the balance block, and the ratio of the length of the connecting rod oil groove to the circumference of the inner side wall of the connecting rod connecting end along the circumferential direction of the inner side wall of the connecting rod connecting end is 1:2-4: 5.
In some embodiments, along the circumference of the inner side wall of the connecting rod connecting end, the ratio of the length of the connecting rod oil groove to the circumference of the inner side wall of the connecting rod connecting end is 3:4, an included angle between a connecting line of one end point of the connecting rod oil groove in the length direction and the bottom center of the connecting rod connecting end and the rod body is 0-90 degrees, and an included angle between a connecting line of the other end point of the connecting rod oil groove in the length direction and the bottom center of the connecting rod connecting end and the rod body is 0-90 degrees.
In some embodiments, the oil drainage hole is a strip-shaped hole arranged along the circumferential direction of the outer side wall of the eccentric shaft, and the ratio of the length of the oil drainage hole to the circumference of the outer side wall of the eccentric shaft is 1-1:8.
In some embodiments, the width of the drainage holes is 0.5mm to 1.5mm.
In some embodiments, the balance block is further provided with a holding groove towards the top of the eccentric shaft, the holding groove is communicated with the connecting rod oil groove, the balance block is further provided with at least one oil leakage hole penetrating through the top and the bottom of the balance block, and the oil leakage hole is communicated with the holding groove.
In some embodiments, the holding groove is an arc-shaped groove or an annular groove disposed around the eccentric shaft, and the balance block is provided with two oil leakage holes respectively located on two sides of the eccentric shaft.
In some embodiments, an eccentric oil groove is further arranged on the outer side wall of the eccentric shaft, one end of the eccentric oil groove is communicated with the oil drainage hole, and the other end of the eccentric oil groove extends to the upper end part of the eccentric shaft, which is far away from the balance block, in a spiral manner and does not exceed the connecting rod connecting end; the spiral direction of the eccentric oil groove is opposite to the rotation direction of the eccentric shaft.
One or more technical solutions in the crankshaft assembly provided by the embodiment of the present invention have at least one of the following technical effects: compared with the prior art, the crankshaft assembly is provided with the oil drainage hole on the eccentric shaft, and the connecting rod connecting end of the connecting rod is provided with the connecting rod oil groove, wherein the oil drainage hole is communicated with the oil pumping channel of the eccentric shaft, the connecting rod oil groove is communicated with the gap between the eccentric shaft and the balance block, and when the eccentric shaft rotates, the oil drainage hole can rotate to be communicated with or staggered with the connecting rod oil groove. The eccentric shaft rotates the in-process, and the lubricating oil that gets into in the pump oil passageway can flow through the draining hole, and wherein, when the eccentric shaft rotates to draining hole and the connecting rod oil groove stagger, the lubricating oil that flows from the draining hole receives the hindrance of the inside wall of connecting rod link and can't throw away in a large number, only has in the clearance between the inside wall of few part's lubricating oil entering connecting rod link and the outside wall of eccentric shaft this moment for lubricated connecting rod link and eccentric shaft. And when the eccentric shaft rotated to the draining hole and communicated with the connecting rod oil groove, the lubricating oil flowing out of the draining hole further flowed into the connecting rod oil groove and flowed out of the gap between the connecting rod connecting end and the balance block, and at the moment, the lubricating oil flowing out of the draining hole could not flow into the cylinder hole of the cylinder. Therefore, the lubricating oil pumped to the cylinder hole in the whole operation period of the crankshaft can be reduced, so that excessive oil pumping of the crankshaft under a high-speed operation working condition is avoided, the variable frequency compressor using the crankshaft assembly is ensured to reduce the oil output on the basis of ensuring the lubrication of the cylinder hole, and continuous and stable oil supply under a high-frequency working condition is realized.
The other technical scheme of the invention is as follows: an inverter compressor is provided, which comprises the crankshaft.
The variable frequency compressor provided by the embodiment of the invention has the beneficial effects that: compared with the prior art, the variable frequency compressor provided by the invention has the advantages that by using the crankshaft assembly, the compressor can realize continuous and stable oil supply under high-frequency and low-frequency working conditions, the cylinder hole can be effectively lubricated, and the condition of excessive oil pumping can be avoided under the high-frequency working condition, so that the compressor can run more stably and efficiently.
The invention also adopts the technical scheme that: a refrigeration device is provided, and the refrigeration device comprises the inverter compressor.
The refrigeration equipment provided by the embodiment of the invention has the beneficial effects that: compared with the prior art, the refrigeration equipment provided by the invention has the advantages that due to the adoption of the variable frequency compressor, the refrigeration equipment can stably run under low-frequency and high-frequency working conditions, the running stability of the refrigeration equipment is improved, the refrigeration effect is improved, the running energy consumption is lower, and the service life is prolonged.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the embodiments or the prior art descriptions will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise.
FIG. 1 is a schematic structural view of a crankshaft assembly with an oil drain hole in communication with a connecting rod oil groove according to an embodiment of the present invention;
FIG. 2 is an enlarged schematic view of FIG. 1 at A;
FIG. 3 is a schematic view of the crankshaft assembly shown in FIG. 1 with the drain holes staggered with respect to the connecting rod oil grooves;
FIG. 4 is an enlarged schematic view of FIG. 3 at B;
FIG. 5 is a schematic illustration of a crankshaft of the crankshaft assembly shown in FIG. 1;
FIG. 6 is a schematic view of a connecting rod of the crankshaft assembly shown in FIG. 1;
FIG. 7 is a top view of a portion of the linkage shown in FIG. 6;
FIG. 8 is a top view of the crankshaft assembly shown in FIG. 1;
FIG. 9 is a schematic view of a counterbalance of the crankshaft assembly shown in FIG. 1.
In the figures, the various figures are mainly marked:
10. a crankshaft; 11. a main shaft; 111. a main shaft oil groove; 112. a first oil hole; 113. a second oil hole; 12. an eccentric shaft; 121. An oil pumping channel; 122. an oil drainage hole; 123. an eccentric oil groove; 13. a counterbalance; 131. accommodating grooves; 132. an oil leak hole; 20. A connecting rod; 21. a connecting rod connecting end; 211. a connecting rod oil groove; 22. a connecting rod driving end; 23. a rod body; 231. a connecting rod oil duct; 30. A piston; 40. a cylinder bore; 50. a crankcase; 60. and a bearing.
Detailed Description
In order to make the technical problems, technical solutions and advantageous effects to be solved by the present invention more clearly apparent, the present invention is further described in detail below with reference to fig. 1 to 9 and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or be indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or be indirectly connected to the other element.
The terms "length," "width," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like are used in an orientation or positional relationship indicated based on the orientation or positional relationship shown in the drawings for the sake of simplicity of description only, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed in a particular orientation, and be constructed in operation, and are not to be construed as limiting the invention.
The terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. The features defined as "first", "second" may explicitly or implicitly include one or more of the features and "a plurality" means two or more.
Reference in the specification to "one embodiment," "some embodiments," or "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment is included in one or more embodiments of the invention. The appearances of the phrases "in one embodiment," "in some embodiments," "in other embodiments," or the like in various places in the specification are not necessarily all referring to the same embodiment, but rather "one or more but not all embodiments" unless specifically stated otherwise. The particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments.
Generally, a conventional compressor generally includes a casing, a crankcase, a crankshaft, an oil pump, a connecting rod, a cylinder, a piston, a driving motor, and the like, wherein an oil sump storing lubricating oil is disposed at the bottom of the casing, the crankshaft includes a main shaft drivingly connected to the driving motor, a balance weight (also called a crank) connected to one end of the main shaft, and an eccentric shaft eccentrically connected to one end of the main shaft through the balance weight, a lubricating oil supply system (referred to as an oil supply system) is disposed inside the crankshaft, the oil pump is disposed at the bottom of the main shaft at the end away from the eccentric shaft, and an oil outlet of the oil pump is communicated with the oil supply system inside the crankshaft. The cylinder is arranged in the crankcase, the piston is arranged at the cylinder hole of the cylinder, the crankshaft is arranged in the crankcase, and the connecting rod is connected with the eccentric shaft of the crankshaft and the piston. When the compressor works, the crankshaft of the driving motor rotates, the crankshaft drives the piston to do reciprocating linear motion in the cylinder hole through the connecting rod, so that refrigerant in the cylinder is compressed, meanwhile, lubricating oil at the bottom of the shell can be conveyed and guided to each friction pair of the compressor through the lubricating oil supply system to be lubricated, so that friction loss during operation among all parts in the compressor is reduced, meanwhile, the lubricating oil also has a certain cooling effect, and therefore the oiling amount of the crankshaft has important influence on normal operation of the compressor.
For the frequency conversion compressor, the output driving energy can be adjusted by continuously changing the running speed according to the working requirement, and the lower the rotating speed is, the lower the power consumption is, so the frequency conversion compressor has the advantages of high efficiency and energy saving. In the related art, based on the low-frequency development of the compressor, the lubricating oil supply system of the existing inverter compressor generally has a strong oil pumping capability, for example, an oil pump with a large oil pumping head is used, so as to ensure that sufficient lubricating oil can be supplied under the low-frequency working condition; and when the compressor operates under high-frequency high-rotating speed, because lubricating oil supply system's the ability of oiling is strong, lubricating oil supply system excessive pump oil under the high-speed operating mode, makes the compressor increase of oil mass of spouting under the high-frequency state, and the income power efficiency of compressor increases to lead to lubricating oil supply system to appear the discontinuous condition of pump oil, influence lubricated effect, the operating mode of variable frequency compressor under high-rotating speed is bad.
The lubricating oil supply system is arranged on the basis of the requirement of the compressor, meanwhile, the frequency conversion compressor has two operation working conditions of high frequency and low frequency, the oil pumping capacity of the lubricating oil supply system needs to be improved for meeting the requirement of sufficient supply of lubricating oil under the low-frequency working condition, and under the high-frequency working condition, in order to avoid excessive oil pumping, the high-frequency oil supply quantity of the lubricating oil supply system needs to be reduced, and the oil pumping quantity of the compressor is ensured to be always kept in a relatively moderate range when the compressor operates at high frequency. Based on the above, the embodiment of the invention optimally designs the crankshaft assembly of the variable frequency compressor, improves the oiling amount of lubricating oil of the lubricating oil supply system at high rotating speed, and provides the lubricating oil supply system capable of stably and continuously supplying oil under low-frequency and high-frequency working conditions. The crankshaft assembly of the present invention will be described in detail with reference to specific embodiments.
Please refer to fig. 1-6. Fig. 1 and fig. 3 are schematic structural diagrams of a crankshaft assembly provided in an embodiment of the present invention in two rotation states, respectively, a partial structure in the diagrams is a perspective structure to show a flow path of lubricating oil, in fig. 1, an oil drainage hole 122 is communicated with a connecting rod oil groove 211, and in fig. 3, the oil drainage hole 122 is staggered with the connecting rod oil groove 211; FIG. 2 is an enlarged schematic view at A in FIG. 1; FIG. 4 is an enlarged schematic view of FIG. 3 at B; fig. 5 is a schematic structural view of a crankshaft 10 of the crankshaft assembly according to the present embodiment; fig. 6 is a schematic structural view of the connecting rod 20 of the crankshaft assembly according to the present embodiment, in which the dotted arrow indicates the rotation direction of the eccentric shaft 12.
Specifically, as shown in fig. 1, 3 and 5, the present embodiment provides a crankshaft assembly including a crankshaft 10. The crankshaft 10 includes a main shaft 11, an eccentric shaft 12, and a balance block 13, the main shaft 11 is in driving connection with an external driving component, the eccentric shaft 12 is installed at one end of the main shaft 11 through the balance block 13 and is eccentrically arranged with respect to a center line (shown as a center line R in fig. 3) of the main shaft 11, the main shaft 11 is provided with an oil suction inner cavity (not shown) communicated with an outlet of an oil pump (not shown), a main shaft oil groove 111 is provided on an outer side wall of the main shaft 11, an oil pumping channel 121 is provided in the eccentric shaft 12, and the oil pumping channel 121 extends into the main shaft 11 and is communicated with the main shaft oil groove 111.
Specifically, as shown in fig. 5, a first oil hole 112 and a second oil hole 113 are provided on the main shaft 11, the main shaft oil groove 111 communicates with the oil suction inner cavity through the first oil hole 112, and communicates with the pumping oil passage 121 through the second oil hole 113, and one end of the pumping oil passage 121 facing away from the main shaft 11 extends to an end portion of the eccentric shaft 12 facing away from the balance weight 13, and forms an outlet of the pumping oil passage 121.
Thus, when the crankshaft 10 rotates, the oil pump pumps lubricating oil to the oil suction inner cavity, the lubricating oil entering the oil suction inner cavity enters the main shaft oil groove 111 through the first oil hole 112, moves along the main shaft oil groove 111 and flows into the pump oil channel 121 through the second oil hole 113, the lubricating oil entering the pump oil channel 121 moves upward along the channel wall of the pump oil channel 121 under the action of centrifugal force to be thrown out from the outlet of the pump oil channel 121, so that the lubricating oil reaches each running part inside the compressor for lubrication, each running part of the compressor using the crankshaft assembly of the embodiment can run normally, and the lubricating oil cools each part.
As shown in fig. 1 to 4 and fig. 6, the crankshaft assembly of the present embodiment further includes a connecting rod 20, the connecting rod 20 includes a connecting rod connecting end 21 sleeved on the eccentric shaft 12, an oil drainage hole 122 communicating with the pump oil channel 121 is formed in an outer side wall of the eccentric shaft 12, a connecting rod oil groove 211 is formed in an inner side wall of the connecting rod connecting end 21, a gap is formed between the connecting rod connecting end 21 and the balance block 13, the connecting rod oil groove 211 is communicated with the gap, and when the eccentric shaft 12 rotates relative to the connecting rod connecting end 21, the oil drainage hole 122 can rotate to be communicated with or staggered with the connecting rod oil groove 211.
Specifically, in the present embodiment, the size of the connecting rod oil groove 211 is larger than that of the oil drain hole 122, and the height of the upper edge of the opening of the oil drain hole 122 is lower than or equal to the height of the upper edge of the notch of the connecting rod oil groove 211 in the radial direction of the eccentric shaft 12, so as to ensure that the oil drain hole 122 can be rotated to be entirely located in the connecting rod oil groove 211 when the eccentric shaft 12 rotates, thereby communicating with the connecting rod oil groove 211, as shown in fig. 1 and 2; the drain hole 122 can also be rotated to be entirely outside the connecting rod oil groove 211 so as to be offset from the connecting rod oil groove 211, as shown in fig. 3 and 4.
Based on this, in the process of rotation of the eccentric shaft 12, the lubricating oil entering the pump oil channel 121 can flow out through the oil drain hole 122, when the eccentric shaft 12 rotates to the oil drain hole 122 to be communicated with the connecting rod oil groove 211, the lubricating oil flowing out from the oil drain hole 122 further flows into the connecting rod oil groove 211 and flows out from the gap between the connecting rod connecting end 21 and the balance block 13, at this time, the lubricating oil flowing out from the oil drain hole 122 cannot flow to the cylinder hole 40 of the cylinder, so that the lubricating oil pumped to the cylinder hole 40 in the whole operation period of the crankshaft 10 can be reduced, thereby avoiding excessive pump oil of the crankshaft 10 under the high-speed operation condition, ensuring that the variable frequency compressor using the crankshaft assembly of the present invention reduces the oil output on the basis of ensuring lubrication of the cylinder hole 40, and realizing continuous and stable oil supply under the high-frequency condition. When the eccentric shaft 12 rotates to the oil drain hole 122 and the connecting rod oil groove 211 are staggered, the lubricating oil flowing out from the oil drain hole 122 is obstructed by the inner side wall of the connecting rod connecting end 21 and cannot be thrown out in a large amount, and only a small part of the lubricating oil enters the gap between the connecting rod connecting end 21 and the eccentric shaft 12 to lubricate the connecting rod connecting end 21 and the eccentric shaft 12. Thus, by providing the oil drain hole 122 and the link oil groove 211, lubrication between the link connecting end 21 and the eccentric shaft 12 can be increased.
Further, when the eccentric shaft 12 rotates until the oil drain hole 122 communicates with the link oil groove 211, the lubricating oil flowing out from the gap between the link connecting end 21 and the weight 13 cannot be thrown to the components such as the casing, and therefore the amount of oil mist formed by the lubricating oil droplets striking the components such as the casing and being crushed can be reduced, the amount of lubricating oil carried in the refrigerant can be reduced, and the oil discharge amount of the compressor using the crank assembly of the present embodiment can be reduced. In another embodiment of the present invention, referring to fig. 2, 5 and 6, the oil drainage hole 122 is disposed at the lower end of the eccentric shaft 12 facing the balance weight 13 and is located at the side of the eccentric shaft 12 away from the center line of the main shaft 11 (specifically, since the eccentric shaft 12 is eccentrically disposed with respect to the main shaft 11, one side of the two opposite sides of the eccentric shaft 12 is close to the center line of the main shaft 11, and the other side is away from the center line of the main shaft), and the connecting rod oil groove 211 is disposed at the lower end of the connecting rod connecting end 21 facing the balance weight 13. During the rotation of the eccentric shaft 12, the centrifugal force applied to the eccentric shaft 12 at a position farther from the center line of the main shaft 11 is larger, and thus, the oil drain hole 122 is provided at a position where the eccentric shaft 12 is farther from the center line of the main shaft 11, so that the amount of the lubricating oil flowing out from the oil drain hole 122 can be increased. And set up draining hole 122 in the lower extreme of eccentric shaft 12, set up connecting rod oil groove 211 in the lower extreme of connecting rod link 21, lubricating oil can flow to the clearance that flows out between connecting rod link 21 and balancing piece 13 with shorter distance, avoids lubricating oil to block up in draining hole 122 and connecting rod oil groove 211, and leads to lubricating oil still can't continuous when draining hole 122 and connecting rod oil groove 211 communicate.
In another embodiment of the present invention, as shown in fig. 1, fig. 2 and fig. 5, an eccentric oil groove 123 is further provided on the outer side wall of the eccentric shaft 12, one end of the eccentric oil groove 123 is communicated with the oil drain hole 122, the other end of the eccentric oil groove 123 extends spirally to the upper end portion of the eccentric shaft 12 away from the balance weight 13, and the lubricating oil flowing out from the oil drain hole 122 can flow into the eccentric oil groove 123, so as to increase the amount of the lubricating oil entering the gap between the eccentric shaft 12 and the connecting rod connecting end 21, and better lubricate the eccentric shaft 12 and the connecting rod connecting end 21 with the rotation of the eccentric shaft 12. Further, the eccentric oil groove 123 extends spirally to the upper end portion of the eccentric shaft 12 not beyond the connecting rod end 21, i.e., the lubricating oil is confined by the connecting rod end 21 in the gap between the eccentric shaft 12 and the connecting rod end 21 and cannot flow out through the eccentric oil groove 123.
In the present embodiment, as shown in fig. 1, 2 and 5, the spiral direction of the eccentric oil groove 123 is opposite to the rotation direction of the eccentric shaft 12, for example, as shown in fig. 5, when the eccentric shaft 12 rotates clockwise, the eccentric oil groove 123 is spirally arranged counterclockwise. Thus, when the lubricant oil enters the eccentric oil groove 123, the lubricant oil is ensured to be spirally raised along the eccentric oil groove 123 by the viscous force of the inner side wall of the connecting rod end 21 and the friction force between the inner side wall of the connecting rod end 21 and the outer side wall of the eccentric shaft 12, thereby sufficiently lubricating the eccentric shaft 12 and the connecting rod end 21.
In another embodiment of the present invention, as shown in fig. 6, the connecting rod 20 further includes a connecting rod driving end 22 disposed opposite to the connecting rod connecting end 21 and connected to the piston 30, and a rod body 23 having two ends respectively connected to the connecting rod connecting end 21 and the connecting rod driving end 22. The rod body 23 is internally provided with the connecting rod oil duct 231, two ends of the connecting rod oil duct 231 respectively penetrate through the inner side wall of the connecting rod connecting end 21 and the inner side wall of the connecting rod driving end 22, and in the rotating process of the eccentric shaft 12, the eccentric oil groove 123 can be rotated to be communicated with the first end of the connecting rod oil duct 231, so that lubricating oil flowing out of the oil drainage hole 122 can enter the connecting rod oil duct 231 through the eccentric oil groove 123 and flow to the inner side wall of the connecting rod driving end 22, and therefore the connecting rod driving end 22 and the piston 30 pin sleeved in the connecting rod driving end 22 are lubricated.
In another embodiment of the present invention, as shown in fig. 5, the oil drainage hole 122 is a strip-shaped hole disposed along the circumferential direction of the outer sidewall of the eccentric shaft 12, and the outflow of the lubricating oil from the oil drainage hole 122 is influenced by the centrifugal force of the eccentric shaft 12 and its own gravity, so that the outflow of the lubricating oil is concentrated on the oil drainage hole 122 toward the bottom of the counterweight 13, and thus, the oil drainage hole 122 is provided with a strip-shaped long hole, which is helpful for increasing the amount of the lubricating oil flowing out through the oil drainage hole 122, so that the entire opening of the oil drainage hole 122 can be used for oil drainage.
In addition, the ratio of the length of the oil drainage hole 122 to the circumference of the outer side wall of the eccentric shaft 12 is set to be 1 to 1:8, that is, the length of the oil drainage hole 122 is reasonably set to ensure the amount of the discharged lubricating oil, in a specific embodiment, the length of the oil drainage hole 122 may be 0.1, 0.11, 0.115, 0.118, 0.12, 0.122, or 0.125 times of the circumference of the outer side wall of the eccentric shaft 12, and the like, and when the oil drainage hole is specifically designed, the oil drainage hole may be set according to the size of the eccentric shaft 12 and the amount of the lubricating oil which needs to be discharged through the oil drainage hole 122, and the setting is not limited herein.
In the present embodiment, as shown in fig. 5, the width of the oil release hole 122 is 0.5mm to 1.5mm along the axial direction of the eccentric shaft 12, that is, the width of the oil release hole 122 is reasonably set to ensure smooth outflow of the lubricating oil. In a specific embodiment, the width of the oil drainage hole 122 may be 0.5mm, 0.6mm, 0.8mm, 1.0mm, 1.2mm, 1.5mm, or the like. The specific design may be set according to the size of the eccentric shaft 12, the length of the oil release hole 122, and the amount of lubricating oil to be released through the oil release hole 122, and is not limited herein.
In another embodiment of the present invention, as shown in fig. 6, the connecting rod oil groove 211 is disposed on a side portion of the connecting rod connecting end 21 away from the connecting rod driving end 22, that is, the oil drainage hole 122 is communicated with the connecting rod oil groove 211 on a side away from the connecting rod driving end 22, and is staggered with the connecting rod oil groove 211 on a side toward the connecting rod driving end 22, as shown in fig. 1 and fig. 3. In this way, since the oil drain hole 122 is provided on the side of the eccentric shaft 12 away from the center line of the main shaft 11, when the oil drain hole 122 communicates with the connecting rod oil groove 211, the side of the eccentric shaft 12 away from the center line of the main shaft 11 deviates from the connecting rod driving end 22, i.e., from the cylinder hole 40 of the cylinder, as shown in fig. 1 and 2, at this time, most or even all of the lubricating oil is drained through the oil drain hole 122 and the connecting rod oil groove 211, and only a small amount or even almost no lubricating oil can be thrown from the outlet of the pump oil passage 121 to the cylinder hole 40. On the contrary, when the oil drainage hole 122 is staggered from the connecting rod oil groove 211, one side of the eccentric shaft 12 away from the central line of the main shaft 11 moves to the connecting rod driving end 22, i.e. to the cylinder hole 40 of the cylinder, as shown in fig. 3 and 4, at this time, most or even all of the lubricating oil is thrown out through the outlet of the pump oil passage 121 and thrown to the cylinder hole 40 under the action of centrifugal force, thereby ensuring that when the oil drainage hole 122 is staggered from the connecting rod oil groove 211, a sufficient amount of lubricating oil can be thrown out from the outlet of the pump oil passage 121 and enter the cylinder hole 40 to lubricate the cylinder hole 40.
In the present embodiment, as shown in fig. 1 and 6, the connecting rod oil groove 211 is a notch provided at the bottom of the connecting rod connecting end 21 facing the counterweight 13, that is, the connecting rod oil groove 211 is actually a notch concavely provided at the bottom of the inner side wall of the connecting rod connecting end 21, and the ratio of the length of the connecting rod oil groove 211 to the circumference of the inner side wall of the connecting rod connecting end 21 along the circumferential direction of the inner side wall of the connecting rod connecting end 21 is 1:2-4:5, that is, the connecting rod oil groove 211 is provided at the position of 1/2 to 4/5 of the inner side wall of the connecting rod connecting end 21, so that the oil drainage hole 122 has 1/2 to 4/5 of the time to communicate with the connecting rod oil groove 211 and the other time is offset from the connecting rod oil groove 211 during the rotation of the eccentric shaft 12. Thus, in one rotation period of the eccentric shaft 12, the length of the communication time between the oil drain hole 122 and the connecting rod oil groove 211 can be controlled by setting the length of the connecting rod oil groove 211, so that the amount of lubricating oil leaking through the oil drain hole 122 is controlled, the amount of lubricating oil flowing out from the outlet of the pump oil passage 121 and thrown to the cylinder hole 40 is controlled within a proper range, and excessive oil supply or insufficient oil supply is avoided. During actual production, the length of the connecting rod oil groove 211 can be designed according to the lubricating oil amount required by the compressor under high-frequency and low-frequency working conditions, so that the compressor can be guaranteed to supply oil in sufficient amount under all working conditions. In some embodiments, the length of the link oil groove 211 may be 0.5, 0.55, 0.6, 0.65, 0.7, 0.75, or 0.8 times the circumference of the inner sidewall of the link connecting end 21, etc.
In the present embodiment, by designing the sizes of the drain hole 122 and the link oil groove 211, two extreme states of the supply of the lubricating oil can be realized as long as the size of the drain hole 122 is set sufficiently large and the communication time of the link oil groove 211 with the drain hole 122 is set sufficiently large. In one state, at the stage that the oil drain hole 122 and the connecting rod oil groove 211 are staggered, lubricating oil is blocked by the inner side wall of the connecting section of the connecting rod 20 and cannot smoothly flow out of the oil drain hole 122, and at the moment, the lubricating oil entering the pump oil channel 121 and all the lubricating oil continuously and continuously pass through the outlet of the pump oil channel 121 and are thrown to the cylinder hole 40 under the action of centrifugal force so as to lubricate the cylinder hole 40; in the other state, in the stage that the oil drainage hole 122 is communicated with the connecting rod oil groove 211, the lubricating oil entering the pump oil passage 121 can continuously and completely flow out through the oil drainage hole 122, at this time, no lubricating oil can move to the outlet of the pump oil passage 121 to be thrown out, namely no lubricating oil enters the cylinder hole 40, and at this time, the lubrication of the cylinder hole 40 is realized by the lubricating oil entering the cylinder hole 40 in the former state.
For example, referring to fig. 7 and 8, the dimensions of the connecting rod oil groove 211 and the oil drain hole 122 in one embodiment are described. Fig. 7 is a plan view of a partial structure of a connecting rod 20 of the crankshaft assembly of the present embodiment, and fig. 8 is a plan view of the crankshaft assembly of the present embodiment.
In this embodiment, the ratio of the length of the link oil groove 211 to the inner sidewall circumference of the link connecting end 21 is 3:4. Furthermore, a connecting line (as shown by line L in FIG. 5) between one end point of link oil groove 211 in the longitudinal direction (the center position of one end part of link oil groove 211 in the longitudinal direction) and the center of the bottom of link connecting end 21 is formed 1 Shown) and the rod body 23 (specifically, as indicated by line L in FIG. 7) 2 The center line of the rod 23 as shown) is included 1 Is 0 to 90 degrees, and makes the connecting rod oil groove 211 along the other end point of the length direction (the central position of the other end part of the connecting rod oil groove 211 in the length direction) and the connecting rod connecting end 21 bottom center connecting line (as the line L in figure 7 3 Shown) andangle alpha of the rod 23 2 Is 0 to 90 degrees. I.e. the connecting rod oil groove 211 is connected with the connecting rod connecting end 21 by a connecting line (as shown by line L in FIG. 7) 1 Shown), and a line connecting the other end point of the link oil groove 211 in the length direction and the center of the bottom of the link connecting end 21 (as indicated by line L in fig. 7) 3 Shown) is 90 deg., and the portion of the link coupling end 21 where the link oil groove 211 is not provided occupies 1/4 of the circumference of the inner side wall of the link coupling end 21.
Thus, when the eccentric shaft 12 rotates to the position where the oil release hole 122 is staggered with the connecting rod oil groove 211, that is, the oil release hole 122 moves to the range of 0-90 ° on both sides of the rod 23 (as shown by the included angle β in fig. 7), all the lubricating oil is thrown out to the cylinder hole 40 through the outlet of the pump oil channel 121, which corresponds to the oil outlet area of the pump oil channel 121, as shown by the two dotted lines L in fig. 8 4 And L 5 A defined area W. When eccentric shaft 12 rotates until oil drain hole 122 communicates with link oil groove 211, all the lubricating oil is drained through oil drain hole 122 and link oil groove 211, and at this time, no lubricating oil is thrown out from the outlet of pump oil passage 121, that is, no oil is drained from pump oil passage 121 in the range, which corresponds to the oil-drainage-free region of pump oil passage 121, except for region W in fig. 8. It should be noted that, in the present embodiment, theoretically, the angle value of the oil outlet area W in fig. 8 should be equal to the value of the included angle β in fig. 7, but when the lubricant is thrown out from the outlet of the oil pumping channel 121, the lubricant will be deflected toward the rod body 23 by the centrifugal force of the eccentric shaft 12, so that the angle value of the oil outlet area W actually discharging the lubricant is slightly smaller than the value of the theoretical included angle β.
In an embodiment, the included angle α is 1 Can be 0 degree, 30 degree, 44 degree, 60 degree, 75 degree, 80 degree or 90 degree, and the included angle alpha is 2 Can be 0 °, 30 °, 45 °, 60 °, 75 °, 80 °, 90 °, etc., and the design of the above-mentioned included angle can be selected according to the rotation direction of the eccentric shaft 12 and the rotation speed. For example, when the eccentric shaft 12 rotates clockwise, the lubricant oil thrown out from the outlet of the pump oil passage 121 is subjected to a centrifugal force in the clockwise direction, and the faster the rotation speed of the eccentric shaft 12 is, the more centrifugal force the lubricant oil is subjected to when thrown outThe eccentric shaft 12 can be more deviated from the rod body 23 to move after being thrown out, so that when the rotation speed of the eccentric shaft 12 is high, the whole part of the connecting rod connecting end 21 without the connecting rod oil groove can be positioned at the upper right of the rod body 23, even if the included angle alpha is formed 1 Is 90 DEG and includes an angle alpha 2 Is 0 ° as shown in fig. 7 (b); on the contrary, when the eccentric shaft 12 rotates counterclockwise, the lubricant thrown from the outlet of the pump oil passage 121 is subjected to the centrifugal force in the counterclockwise direction, and when the rotational speed of the eccentric shaft 12 is fast, the whole of the portion of the connecting rod end 21 where the connecting rod oil groove is not provided can be positioned at the lower left of the rod body 23, even though the above-mentioned angle α is included 1 Is 0 DEG and an included angle alpha 2 At 90 °, as shown in fig. 7 (c); while the centrifugal force to which the lubricating oil is thrown out decreases as the rotational speed of the eccentric shaft 12 decreases, the α can be adjusted in this case 1 And alpha 2 To ensure that the oil is still thrown against the cylinder bore 40 at lower rotational speeds, as shown in fig. 7 (a).
In another embodiment of the present invention, please refer to fig. 1, fig. 5 and fig. 9, wherein fig. 9 is a schematic structural diagram of a balance weight 13 of a crankshaft 10 of the crankshaft assembly according to the present embodiment.
In this embodiment, the balance weight 13 is further provided with a receiving groove 131 towards the top of the eccentric shaft 12, the receiving groove 131 is communicated with the connecting rod oil groove 211, namely, the receiving groove 131 is located under the connecting rod oil groove 211, the balance weight 13 is further provided with at least one oil leakage hole 132, and the oil leakage hole 132 penetrates through the top and the bottom of the balance weight 13 and is communicated with the receiving groove 131. Thus, the lubricating oil flowing out of the oil drain hole 122 enters the connecting rod oil groove 211, and then further falls into the receiving groove 131, and flows out through the oil drain hole 132 to contact the bearing 60 sleeved outside the main shaft 11, thereby lubricating the bearing 60. So, set up holding tank 131 and oil leak hole 132 on balancing piece 13 for the guide gets into the lubricating oil part in connecting rod oil groove 211 and flows to and contact with bearing 60, thereby lubricated bearing 60, thereby make the compressor that uses the crankshaft assembly of this embodiment under the prerequisite of guaranteeing that cylinder hole 40 is lubricated, can also increase the lubrication to bearing 60, reduce the friction and the noise that bearing 60 goes out, improve the rotation compliance of main shaft 11.
In the present embodiment, as shown in fig. 5 and 9, the accommodating groove 131 is an arc-shaped groove or an annular groove disposed around the eccentric shaft 12, and two oil leakage holes 132 are disposed on the balance weight 13 and located on two sides of the eccentric shaft 12 respectively. The lubricating oil that gets into holding tank 131 can flow out to bearing 60 department through two oil leak holes 132 promptly to the multiple spot lubrication to bearing 60 is realized, and bearing 60 lubrication effect is better.
In the present embodiment, as shown in fig. 5 and 9, the oil leak hole 132 is a strip-shaped hole, one long side of which is connected to the side of the receiving groove 131, the lubricating oil flows in from the long side of the oil leak hole 132, and the width of the oil leak hole 132 is 0.5mm to 1.5mm in the radial direction of the eccentric shaft 12, ensuring that a proper amount of lubricating oil is supplied to lubricate the bearing 60. In a specific embodiment, the width of the oil leakage hole 132 may be 0.5mm, 0.8mm, 1.0mm, 1.2mm, or 1.5mm, and the like, and may be set according to the amount of the lubricating oil required by the bearing 60 when designing, and is not limited herein.
It is understood that in other embodiments, the oil leakage hole 132 may be a circular hole, and in this case, the oil leakage hole 132 is disposed at the bottom of the receiving groove 131, so that the lubricant oil entering the receiving groove 131 directly flows out from the bottom of the receiving groove through the oil leakage hole 132. In this case, the diameter of the oil leakage hole 132 may be set to 0.5mm to 1.5mm, specifically, 0.5mm, 0.8mm, 1.0mm, 1.2mm, or 1.5mm.
According to the crankshaft assembly of each embodiment of the invention, lubricating oil pumped to the cylinder hole 40 in the whole operation period of the crankshaft 10 can be reduced, so that excessive oil pumping of the crankshaft 10 under a high-speed operation working condition is avoided, the variable frequency compressor using the crankshaft assembly of each embodiment is ensured, the oil output is reduced on the basis of ensuring the lubrication of the cylinder hole 40, continuous and stable oil supply under a high-frequency working condition is realized, the variable frequency compressor can be ensured to efficiently and reliably operate under the high-frequency and low-frequency working conditions, the variable frequency operation of the variable frequency compressor is more stable, and the energy consumption can be further saved.
The invention further provides an inverter compressor which comprises the crankshaft assembly.
According to the variable frequency compressor provided by the embodiment of the invention, by using the crankshaft assembly of each embodiment, continuous and stable oil supply can be realized for the compressor under high-frequency and low-frequency working conditions, the cylinder hole can be effectively lubricated, and the condition of excessive oil pumping can not occur under the high-frequency working condition, so that the operation of the compressor is more stable and efficient.
It can be understood that the inverter compressor also has other technical effects of the crankshaft assembly provided by the above embodiments, and the details are not described herein.
The invention further provides refrigeration equipment which comprises the inverter compressor.
According to the refrigeration equipment provided by the embodiment of the invention, due to the adoption of the variable frequency compressors of the embodiments, the refrigeration equipment can stably operate under low-frequency and high-frequency working conditions, the operation stability of the refrigeration equipment is improved, the refrigeration effect is improved, the operation energy consumption is lower, and the service life is prolonged.
It can be understood that the refrigeration equipment also has other technical effects of the inverter compressor provided by the above embodiments, and details are not described herein.
In a specific embodiment, the refrigeration device may be a refrigerator, an air conditioner, or the like.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.

Claims (12)

1. The utility model provides a crankshaft assembly, includes bent axle and connecting rod, the bent axle includes main shaft, balancing piece and eccentric shaft, the eccentric shaft passes through balancing piece eccentric mounting in the one end of main shaft, the main shaft is provided with the main shaft oil groove, be provided with in the eccentric shaft and extend to the main shaft and with the pump oil passageway of main shaft oil groove intercommunication, the export of pump oil passageway extends to lining up the eccentric shaft deviates from the tip of main shaft, the connecting rod including cup joint in the connecting rod link of eccentric shaft, its characterized in that: an oil drainage hole communicated with the oil pumping channel is formed in the outer side wall of the eccentric shaft, a connecting rod oil groove is formed in the inner side wall of the connecting rod connecting end, a gap is formed between the connecting rod connecting end and the balance block, and the connecting rod oil groove is communicated with the gap; when the eccentric shaft rotates relative to the connecting rod connecting end, the oil drainage hole can rotate to be communicated with the connecting rod oil groove or staggered.
2. The crankshaft assembly as in claim 1, wherein: the oil drainage hole is formed in the position, facing the lower end portion of the balance block, of the eccentric shaft and is located on the side portion, away from the central line of the main shaft, of the eccentric shaft, and the connecting rod oil groove is formed in the position, facing the lower end portion of the balance block, of the connecting rod connecting end.
3. The crankshaft assembly as in claim 2, wherein: the connecting rod further comprises a connecting rod driving end and a rod body, wherein the connecting rod driving end is opposite to the connecting rod connecting end, the two ends of the rod body are respectively connected with the connecting rod connecting end and the connecting rod driving end, and the connecting rod oil groove is formed in the side portion, deviating from the connecting rod driving end, of the connecting rod connecting end.
4. The crankshaft assembly as in claim 3, wherein: the connecting rod oil groove is arranged in a gap at the bottom of the inner side wall of the connecting rod connecting end facing the balance block and is along the circumferential direction of the inner side wall of the connecting rod connecting end, and the ratio of the length of the connecting rod oil groove to the circumference of the inner side wall of the connecting rod connecting end is 1:2-4:5.
5. The crankshaft assembly as in claim 4, wherein: the ratio of the length of the connecting rod oil groove to the circumference of the inner side wall of the connecting rod connecting end is 3:4 along the circumferential direction of the inner side wall of the connecting rod connecting end, the included angle between the connecting line of one end point of the connecting rod oil groove in the length direction and the bottom center of the connecting rod connecting end and the rod body is 0-90 degrees, and the included angle between the connecting line of the other end point of the connecting rod oil groove in the length direction and the bottom center of the connecting rod connecting end and the rod body is 0-90 degrees.
6. The crankshaft assembly as in any one of claims 1 to 5, wherein: the oil drainage hole is a strip-shaped hole arranged along the circumferential direction of the outer side wall of the eccentric shaft, and the ratio of the length of the oil drainage hole to the circumference of the outer side wall of the eccentric shaft is 1-1:8.
7. The crankshaft assembly as in claim 6, wherein: the width of the oil drainage hole is 0.5 mm-1.5 mm.
8. The crankshaft assembly as in any one of claims 1 to 5, wherein: the balance block is provided with a connecting rod oil groove, the top of the eccentric shaft is provided with a containing groove, the containing groove is communicated with the connecting rod oil groove, the balance block is provided with at least one oil leakage hole which penetrates through the top and the bottom of the balance block, and the oil leakage hole is communicated with the containing groove.
9. The crankshaft assembly as in claim 8, wherein: the holding tank is an arc-shaped groove or an annular groove arranged around the eccentric shaft, the balance block is provided with two oil leakage holes, and the two oil leakage holes are respectively positioned on two sides of the eccentric shaft.
10. The crankshaft assembly as in any one of claims 2 to 5, wherein: an eccentric oil groove is further formed in the outer side wall of the eccentric shaft, one end of the eccentric oil groove is communicated with the oil drainage hole, and the other end of the eccentric oil groove extends to the upper end portion, away from the balance block, of the eccentric shaft in a spiral mode and does not exceed the connecting end of the connecting rod; the spiral direction of the eccentric oil groove is opposite to the rotation direction of the eccentric shaft.
11. An inverter compressor, characterized in that: comprising a crankshaft assembly as claimed in any one of claims 1 to 10.
12. A refrigeration apparatus, characterized by: comprising the inverter compressor of claim 11.
CN202110608285.7A 2021-06-01 2021-06-01 Crankshaft assembly, variable frequency compressor and refrigeration equipment Pending CN115434890A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202110608285.7A CN115434890A (en) 2021-06-01 2021-06-01 Crankshaft assembly, variable frequency compressor and refrigeration equipment

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202110608285.7A CN115434890A (en) 2021-06-01 2021-06-01 Crankshaft assembly, variable frequency compressor and refrigeration equipment

Publications (1)

Publication Number Publication Date
CN115434890A true CN115434890A (en) 2022-12-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202110608285.7A Pending CN115434890A (en) 2021-06-01 2021-06-01 Crankshaft assembly, variable frequency compressor and refrigeration equipment

Country Status (1)

Country Link
CN (1) CN115434890A (en)

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