Crankshaft, variable-frequency compressor and refrigeration equipment

Abstract

The present invention belongs to the technical field of compressors, and more specifically, relates to a crankshaft, a variable-frequency compressor, and a refrigeration device. The crankshaft includes a main shaft, a crankshaft, and a crank. The crankshaft is mounted at one end of the main shaft through the crank. The main shaft is provided with an oil suction inner cavity and a distribution oil passage extending through the crankshaft. The outer wall surface of the main shaft is provided with a first spiral oil groove and a second spiral oil groove, one end of which is communicated with the oil suction inner cavity. The other end of the first spiral oil groove deflects towards the central axis of the main shaft to form a first orifice communicating with the distribution oil passage, and the other end of the second spiral oil groove deflects towards the central axis of the main shaft to form a second orifice communicating with the distribution oil passage. Moreover, the deflection depths of the first orifice and the second orifice are approximately equal, and the outlet areas of the two are approximately equal. Thus, when the crankshaft rotates forward or backward at the same speed, it can ensure that the lubricating oil supplied through the first spiral oil groove and the second spiral oil groove is approximately equal, realizing approximately equal oil supply to the crankshaft during forward and reverse rotation at the same speed.

Description

Technical Field

[0001] The present invention belongs to the technical field of compressors, and more particularly, relates to a crankshaft, a variable-frequency compressor, and a refrigeration device. Background Art

[0002] The crankshaft is one of the most important components in various compressors. It bears the force transmitted by the connecting rod, converts it into torque output, and drives other accessories of the compressor to work. Generally, the crankshaft includes a main shaft, a crank, and a crankshaft. An oil groove is provided on the main shaft, and the oil groove forms an oil supply system of the crankshaft with other cavities and hole structures provided on the main shaft and the crankshaft. The oil supply system is used to introduce or discharge lubricating oil such as engine oil into or out of the crankshaft, so as to form a lubricating oil film on the surfaces of moving parts such as the crankshaft, so as to lubricate each moving part and ensure that the moving parts such as the crankshaft can rotate flexibly. In particular, for a variable-frequency compressor, it needs to frequently change frequency and capacity. The motor and crankshaft of the compressor not only need to rotate forward, but often also need to rotate backward. Thus, the oil supply system of the crankshaft not only needs to ensure the oil supply during forward rotation, but also needs to ensure the oil supply during reverse rotation.

[0003] In related technologies, generally two spiral oil grooves with opposite rotation directions are provided on the main shaft, and both spiral oil grooves are communicated with a distribution oil passage extending from the crankshaft into the main shaft. When the crankshaft rotates forward, the lubricating oil is transported to the distribution oil passage through the forward-rotating spiral oil groove and then flows out from the crankshaft. When the crankshaft rotates backward, the lubricating oil is transported through the other reverse-rotating spiral oil groove, so as to realize oil supply under both forward and reverse rotation conditions of the crankshaft. However, although this structure can solve the oil supply problem of the crankshaft under forward and reverse rotation, when it is required to supply substantially the same amount of lubricating oil during forward and reverse rotation of the crankshaft, the related technologies have not given a reasonable solution, so it is difficult to realize substantially equal oil supply during forward and reverse rotation of the crankshaft, resulting in insufficient oil supply in one direction or excessive oil supply in the other direction when the crankshaft rotates forward or backward at the same speed. Summary of the Invention

[0004] The main purpose of the embodiments of the present invention is to provide a crankshaft, a variable-frequency compressor, and a refrigeration device, so as to solve the technical problem that the crankshaft in the prior art is difficult to ensure substantially equal oil supply during forward and reverse rotation at the same speed.

[0005] To achieve the foregoing objectives of the present invention, a lubricating oil system needs to be provided on the crankshaft of the compressor. At the same time, since the compressor has two rotational operating conditions, namely forward rotation and reverse rotation, especially for a variable-frequency compressor, forward and reverse rotations are associated with the frequency modulation and speed regulation of the compressor. Therefore, to achieve equal lubricating oil supply for the variable-frequency compressor under forward and reverse rotations, it is necessary to first satisfy the lubricating oil supply under the two operating conditions of the compressor rotating forward and backward, that is, to ensure that the lubricating oil can flow and supply oil under both the forward and reverse operating conditions of the compressor. On this basis, the inventor further studied the oil supply volume of the lubricating oil under the condition of equal forward and reverse rotation speeds, designed various lubricating oil supply systems that can stably supply oil under forward and reverse operating conditions, and conducted tests on each system separately. Based on the test results, the following technical solutions are provided.

[0006] The technical solution adopted by the present invention is: to provide a crankshaft, including a main shaft, a crankshaft, and a crank. The crankshaft is installed at one end of the main shaft through the crank. An oil suction cavity is provided at the end of the main shaft far from the crankshaft. At the other end of the main shaft connected to the crankshaft, there is a distribution oil passage extending through the crankshaft. On the outer wall surface of the main shaft, there are a first spiral oil groove and a second spiral oil groove with opposite rotation directions. One end of the first spiral oil groove and the second spiral oil groove is connected to the oil suction cavity. The other end of the first spiral oil groove deflects towards the central axis of the main shaft and forms a first hole communicating with a first oil hole. The other end of the second spiral oil groove deflects towards the central axis of the main shaft and forms a second hole communicating with a second oil hole. The hole depth of the first hole is approximately equal to the hole depth of the second hole. The area of the outlet of the first hole communicating with the distribution oil hole is approximately equal to the area of the outlet of the second hole communicating with the distribution oil hole.

[0007] In some embodiments, both the first hole and the second hole extend along the radial direction of the main shaft.

[0008] In some embodiments, the first spiral oil groove rotates a first rotation angle on the outer peripheral wall of the main shaft, and the second spiral oil groove rotates a second rotation angle on the outer peripheral wall of the main shaft. Both the first rotation angle and the second rotation angle do not exceed 180°, and the second rotation angle is greater than the first rotation angle; wherein

[0009] The distribution oil passage is arranged close to the second hole, and along the extension direction of the central axis of the main shaft, the distribution oil passage is offset or inclined towards the first hole.

[0010] In some embodiments, the distribution oil passage is arranged at the central position of the main shaft, and the first spiral oil groove and the second spiral oil groove rotate approximately the same rotation angle on the outer peripheral wall of the main shaft.

[0011] In some embodiments, the first spiral oil groove and the second spiral oil groove have the same pitch.

[0012] In some embodiments, the setting heights of the outlets of the first channel and the second channel along the central axis direction of the main shaft are the same.

[0013] In some embodiments, the setting heights of the outlets of the first channel and the second channel along the central axis direction of the main shaft are different.

[0014] In some embodiments, the setting height of the top of the outlet of the second channel is lower than or equal to the setting height of the bottom of the outlet of the first channel.

[0015] In some embodiments, the main shaft is further provided with an oil inlet hole, and the first spiral oil groove and the second spiral oil groove are communicated with the oil suction inner cavity through the oil inlet hole.

[0016] In some embodiments, the number of the oil inlet holes is one, and the first spiral oil groove and the second spiral oil groove are communicated with the oil suction inner cavity through the same oil inlet hole;

[0017] Alternatively, the number of the oil inlet holes is two, and the first spiral oil groove and the second spiral oil groove are respectively communicated with the oil suction inner cavity through two different oil inlet holes.

[0018] In some embodiments, the distribution oil channel is a straight channel.

[0019] In some embodiments, a section of the distribution oil channel located on the main shaft is a straight channel section, and one end of the distribution oil channel located on the crankshaft is an arc-shaped channel section bent away from the main shaft.

[0020] One or more of the above technical solutions in the crankshaft provided by the embodiments of the present invention at least have the following technical effects: Compared with the prior art, in the crankshaft of the present invention, by providing the first spiral oil groove and the second spiral oil groove with opposite rotation directions on the main shaft, it is ensured that the compressor using this crankshaft can supply lubricating oil through the first spiral oil groove and the second spiral oil groove respectively during forward rotation and reverse rotation. Among them, the first spiral oil groove is communicated with the distribution oil channel through the first channel, and the second spiral oil groove is communicated with the distribution oil channel through the second channel, and it is ensured that the depths of the channels of the first channel and the second channel extending along the main shaft are equal, that is, it is ensured that the ends of the first spiral oil groove and the second spiral oil groove penetrate through the side wall of the main shaft with the same thickness and then communicate with the distribution oil channel, and the outlets of the first channel and the second channel with equal opening areas are formed on the peripheral wall of the distribution oil channel. Thus, since the channel depths of the first channel and the second channel are equal, when the crankshaft rotates forward and backward at the same speed, the resistance suffered by the lubricating oil when entering the distribution oil channel through the two channels is the same, so that it can be ensured that the lubricating oil can flow out from the first channel and the second channel at the same speed. In this way, it can be ensured that when the crankshaft rotates forward and backward at the same speed, the amount of lubricating oil supplied through the first spiral oil groove is approximately equal to the amount of lubricating oil supplied through the second spiral oil groove, so as to realize the equal oil supply of the crankshaft during forward and reverse equal-speed rotation, and avoid the problem of insufficient oil supply in one direction or excessive oil supply in the other direction under the condition of equal-speed rotation.

[0021] Another technical solution of the present invention is to provide a variable-frequency compressor, including the above-mentioned crankshaft.

[0022] The beneficial effects of the variable-frequency compressor provided by the embodiments of the present invention are as follows: Compared with the prior art, by using the above-mentioned crankshaft, when the variable-frequency compressor rotates forward and backward at a constant speed, it can achieve an equal supply of lubricating oil, ensuring that the compressor can operate at a constant speed and efficiently in both forward and reverse rotation directions, reducing the wear of the friction pair or reducing the waste of lubricating oil, ensuring that the compressor can supply oil smoothly under different variable-frequency working conditions, and making the operation of the compressor more stable and efficient.

[0023] Another technical solution of the present invention is to provide a refrigeration device, including the above-mentioned variable-frequency compressor.

[0024] The beneficial effects of the refrigeration device provided by the embodiments of the present invention are as follows: Compared with the prior art, due to the use of the above variable-frequency compressor, the refrigeration device operates more stably, the refrigeration effect is more stable, the operation energy consumption is lower, and the service life is longer. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following will briefly introduce the drawings required for use in the embodiments or the description of the prior art. Obviously, the following drawings are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0026] Figure 1 It is a schematic structural diagram of the crankshaft provided for an embodiment of the present invention;

[0027] Figure 2 For Figure 1 The front view structural diagram of the shown crankshaft;

[0028] Figure 3 For Figure 1 The side view structural diagram of the shown crankshaft;

[0029] Figure 4 It is a schematic structural diagram of the crankshaft provided for another embodiment of the present invention;

[0030] Figure 5 For the sectional view along the Figure 2 A-A line in

[0031] Figure 6 For Figure 4 The partial structural diagram truncated along the B-B line in

[0032] Figure 7Schematic diagram of the positional relationship between the outlet of the first channel and the outlet of the second channel of the crankshaft according to an embodiment of the present invention Figure 1 ;

[0033] Figure 8 Schematic diagram of the positional relationship between the outlet of the first channel and the outlet of the second channel of the crankshaft according to another embodiment of the present invention Figure 2 ;

[0034] Figure 9 Front view structural schematic diagram of the crankshaft provided by still another embodiment of the present invention.

[0035] In the figure, the main reference signs of each drawing are as follows:

[0036] 10, main shaft; 11, oil suction inner cavity; 12, oil distribution channel; 121, straight channel section; 122, arc channel section; 13, first spiral oil groove; 14, second spiral oil groove; 15, first oil hole; 151, first channel; 16, second oil hole; 161, second channel; 17, oil inlet hole; 20, crank; 30, crankshaft; 31, oil outlet hole. Detailed implementation manners

[0037] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention clearer and more understandable, the following further details the present invention in conjunction with the attached Figures 1 - 9 drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0038] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it can be directly on the other element or 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 indirectly connected to the other element.

[0039] It should be understood that the orientation or positional relationship indicated by the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention.

[0040] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, the meaning of "a plurality of" is two or more, unless otherwise specifically defined.

[0041] Reference to "an embodiment", "some embodiments" or "the embodiments" in the description of the present invention means that a particular feature, structure or characteristic described in connection with the embodiment is included in one or more embodiments of the present invention. Thus, statements such as "in an embodiment", "in some embodiments", "in other some embodiments", "in still other embodiments" etc. that appear in different places in this specification are not necessarily all referring to the same embodiment, but mean "one or more but not all of the embodiments", unless otherwise specifically emphasized in another way. In addition, in one or more embodiments, the particular features, structures or characteristics may be combined in any suitable manner.

[0042] Generally, a commonly used compressor typically includes a housing, a crankcase, a crankshaft, an oil pump, a connecting rod, a piston, a piston pin, a valve group and a driving motor, etc. An oil sump storing lubricating oil (also known as refrigerant oil) is provided at the bottom of the housing. The crankshaft includes a main shaft drivingly connected to the driving motor and a crank connected to one end of the main shaft. Generally, a lubricating oil supply system (abbreviated as oil supply system) is provided inside the crankshaft. The oil pump is installed at the bottom of the crankshaft, and the oil pumping outlet of the oil pump is communicated with the oil supply system inside the crankshaft. When the compressor operates, the crankshaft rotates. At this time, by using the centrifugal force during the rotation of the crankshaft and in cooperation with the pumping pressure of the oil pump, the lubricating oil at the bottom of the housing can be transported through the oil supply system and led to each friction pair of the compressor for lubrication, thereby reducing the frictional loss during the operation between the various components inside the compressor. At the same time, the lubricating oil also has a certain cooling effect. Therefore, the oil supply amount of the crankshaft has an important influence on the normal operation of the compressor.

[0043] Since a variable-frequency compressor has two rotational operating conditions of forward rotation and reverse rotation, the oil supply system provided on the crankshaft needs to meet the lubricating oil supply in both the forward rotation along the clockwise direction and the reverse rotation along the counterclockwise direction of the variable-frequency compressor, that is, to ensure that the lubricating oil can be supplied to the friction pairs during both the forward rotation and the reverse rotation of the variable-frequency compressor. On this basis, the embodiments of the present invention further optimize the design of the crankshaft of the variable-frequency compressor, improve the oil supply amount of the lubricating oil under the conditions of equal-speed forward and reverse rotation of the crankshaft, and provide a lubricating oil supply system that can stably supply equal amounts of oil under the conditions of equal-speed forward and reverse rotation. The following will describe the crankshaft of the present invention in detail in combination with specific embodiments.

[0044] Please refer to Figure 1 andFigure 2 , Figure 1 Schematic structural diagram of a crankshaft provided for an embodiment of the present invention Figure 2 Front view structural diagram of the crankshaft provided for the embodiment, in which some structures are perspective structures to show the flow path of the lubricating oil. The crankshaft provided for this embodiment can achieve stable oil supply under low-speed, medium-speed and high-speed rotation, and is suitable for being installed in a compressor, especially an inverter compressor.

[0045] Specifically, as Figure 1 and Figure 2 shown, the embodiment of the present invention provides a crankshaft, which includes a main shaft 10 for connecting with an external driving component, a crank 20 installed at one end of the main shaft 10, and a crankshaft 30 connected to the main shaft 10 through the crank 20. The crankshaft 30 is eccentrically arranged relative to the central axis of the main shaft 10 (such as Figure 2 the center line R shown). An oil suction cavity 11 is provided at one end of the main shaft 10 away from the crankshaft 30. The oil suction cavity 11 extends along the central axis of the main shaft 10. A distribution oil passage 12 is provided at the other end of the main shaft 10 connected to the crankshaft 30. The distribution oil passage 12 extends along the central axis of the main shaft 10 and the end away from the oil suction cavity 11 extends to penetrate through the crankshaft 30. Among them, one end of the oil suction cavity 11 is open for communicating with the oil outlet of the oil pump. The distribution oil passage 12 is communicated with the oil suction cavity 11 and is used to make the lubricating oil flow out of the crankshaft, so that the lubricating oil reaches each rotating component inside the compressor for lubrication, ensuring that each rotating component of the compressor using the crankshaft of this embodiment can operate normally and playing a role in cooling and temperature reduction for each component.

[0046] The outer wall surface of the main shaft 10 is provided with a first spiral oil groove 13 and a second spiral oil groove 14 with opposite spiral directions. In this embodiment, the first spiral oil groove 13 is spirally arranged in the clockwise direction (such as Figure 1 the direction shown by the arrow R2 in Figure 1in the direction indicated by arrow R1), both the first spiral oil groove 13 and the second spiral oil groove 14 have a first end and a second end that are oppositely arranged, and the first ends are all oriented towards the bottom end of the main shaft 10, and the second ends are all oriented towards the top end of the main shaft 10. Among them, the first ends of the two spiral oil grooves are both communicated with the oil suction inner cavity 11. First oil holes 15 and second oil holes 16 are opened on the peripheral wall of the distribution oil passage 12. The second end of the first spiral oil groove 13 is communicated with the distribution oil passage 12 through the first oil hole 15, and the second end of the second spiral oil groove 14 is communicated with the distribution oil passage 12 through the second oil hole 16, so that the oil suction inner cavity 11 is respectively communicated with the distribution oil passage 12 through the first spiral oil groove 13 and the second spiral oil groove 14. In this way, since the first spiral oil groove 13 is spirally arranged in the clockwise direction, when the crankshaft rotates clockwise, the lubricating oil pumped into the oil suction inner cavity 11 by the oil pump enters the first spiral oil groove 13 communicated therewith, and by means of the centrifugal force generated by the clockwise rotation of the main shaft 10, it rises from the first end to the second end and enters the distribution oil passage 12 through the first oil hole 15, and further flows out of the distribution oil passage 12 by means of the centrifugal force of the crankshaft 30. On the contrary, when the crankshaft rotates counterclockwise, the lubricating oil enters the second spiral oil groove 14 from the oil suction inner cavity 11, and rises from its first end to the second section by means of the centrifugal force generated by the counterclockwise rotation of the main shaft 10, then enters the distribution oil passage 12 through the second oil hole 16, and then further flows out of the distribution oil passage 12 by means of the centrifugal force of the crankshaft 30. In this way, for the compressor using the crankshaft of this embodiment, under the forward and reverse operating conditions, the normal oil supply is realized respectively by using the first spiral oil groove 13 and the second spiral oil groove 14 with different spiral directions on the main shaft 10, so that the supply of lubricating oil can be realized under the operating conditions of different rotation directions.

[0047] Further, please refer to Figures 2 - 6 together, in which Figure 3 is Figure 1 a schematic side view structure of the crankshaft provided, Figure 4 is a schematic structure diagram of the crankshaft provided by another embodiment of the present invention, Figure 5 is a sectional view along Figure 2 line A-A in Figure 6 is a partial structure schematic diagram truncated along Figure 4 line B-B in . Some structures in the figure are perspective structures to show the flow path of the lubricating oil.

[0048] In this embodiment, since there is a certain thickness dimension between the outer peripheral wall of the main shaft 10 and the peripheral wall of the distribution oil passage 12, before the second end of the first spiral oil groove 13 communicates with the first oil hole 15, and before the second end of the second spiral oil groove 14 communicates with the second oil hole 16, it is necessary to first deflect towards the inside of the main shaft 10 and penetrate through the part between the outer peripheral wall of the main shaft 10 and the peripheral wall of the distribution oil passage 12. Thus, on the main shaft 10, the second section of the first spiral oil groove 13 deflects towards the central axis of the main shaft 10 to form a first passage 151 communicating with the distribution oil passage 12, and the other end of the second spiral oil groove 14 deflects towards the central axis of the main shaft 10 to form a second passage 161 communicating with the distribution oil passage 12. Among them, the above-mentioned first oil hole 15 and second oil hole 16 are respectively the outlets formed by the first passage 151 and the second passage 161 penetrating through the peripheral wall of the distribution oil passage 12. It should be noted that when the crankshaft of this embodiment rotates and supplies lubricating oil, when the lubricating oil flows in the first spiral oil groove 13 and the second spiral oil groove 14, the centrifugal force generated by the rotation of the main shaft 10 can be used as the power to drive the lubricating oil to rise. And when the lubricating oil flows out from the second end of the first spiral oil groove 13 or the second spiral oil groove 14 and flows into the distribution oil passage 12 through the corresponding first passage 151 or the second passage 161, since the flow direction of the lubricating oil entering the distribution oil passage 12 is opposite to the direction of the centrifugal force, at this time, the centrifugal force generated by the rotation of the main shaft 10 will become the resistance for the lubricating oil to flow through the two passages.

[0049] Thus, in this embodiment, the channel depth of the first passage 151 (such as Figure 2 shown as L1 therein) is set to be approximately equal to the channel depth of the second passage 161 (such as Figure 3 shown as L2 therein), that is, the first passage 151 and the second passage 161 penetrate through the wall of the main shaft 10 with the same length and communicate with the distribution oil passage 12, and the outlet area of the first passage 151 is set to be approximately equal to the outlet area of the second passage 161, that is, the opening areas of the first oil hole 15 and the second oil hole 16 are approximately equal. Thus, on the one hand, it can ensure that the outflow cross-sectional areas of the lubricating oil when entering the distribution oil passage 12 are basically equal; on the other hand, it ensures that the extension lengths of the first passage 151 and the second passage 161 are equal, so that the resistance suffered by the lubricating oil when flowing through the two passages is approximately equal. In the case of the main shaft 10 rotating at a constant speed in the positive or reverse direction, the lubricating oil can flow out from the corresponding first oil hole 15 or second oil hole 16 at approximately the same speed. In this way, since the flow rate of a fluid flowing out from a certain outlet is related to the cross-sectional area of the outlet and the outflow velocity of the fluid when flowing out, that is, Q = v·A, where v is the outflow velocity and A is the outlet cross-sectional area. It can be seen from this that when the orifice areas of the first oil hole 15 and the second oil hole 16 are equal, and the outflow velocities of the lubricating oil from the first oil hole 15 and the second oil hole 16 are equal, it can be ensured that the amounts of the lubricating oil flowing out from the first oil hole 15 and the second oil hole 16 are also equal.

[0050] Thus, by setting the first channel 151 and the second channel 161 to have substantially equal extension depths and communicating with the first oil hole 15 and the second oil hole 16 having substantially equal opening areas respectively, it can be ensured that when the crankshaft of this embodiment rotates forward and backward at a certain speed, substantially equal lubricating oil supply amounts can be obtained, so as to meet the lubrication requirements of each friction pair in the compressor at this rotational speed. It should be noted that since the equal supply of lubricating oil does not require the lubricating oil amounts supplied twice to be exactly equal, but only needs to ensure that the supply amount can just meet the lubrication requirements. Therefore, "the deflection depth of the first channel 151 is substantially equal to the deflection depth of the second channel 161" in this embodiment means that within a certain processing error, the deflection depths of the two channels are basically equal, rather than requiring the two lengths to be exactly equal; "the outlet area of the first channel is substantially equal to the outlet area of the second channel" in this embodiment means that within a certain processing error, the areas of the two outlets (i.e., the first oil hole 15 and the second oil hole 16) are basically equal, rather than requiring the areas of the two to be exactly equal.

[0051] Based on this, for the crankshaft of the embodiment of the present invention, by providing the first spiral oil groove 13 and the second spiral oil groove 14 with opposite rotation directions on the main shaft 10, it is ensured that the compressor using this crankshaft can supply lubricating oil through the first spiral oil groove 13 and the second spiral oil groove 14 respectively during forward and reverse rotations. Among them, the first spiral oil groove 13 communicates with the distribution oil channel 12 through the first channel 151, the second spiral oil groove 14 communicates with the distribution oil channel 12 through the second channel 161, and it is ensured that the channel depths of the first channel 151 and the second channel 161 in the extending channel of the main shaft 10 are equal, that is, it is ensured that the ends of the first spiral oil groove 13 and the second spiral oil groove 14 penetrate through the side wall of the main shaft 10 with the same thickness and then communicate with the distribution oil channel 12, and first oil holes 15 and second oil holes 16 with substantially equal opening areas are formed on the peripheral wall of the distribution oil channel 12. Thus, since the channel depths of the first channel 151 and the second channel 161 are equal, when the crankshaft rotates forward and backward at the same speed, the resistance suffered by the lubricating oil when entering the distribution oil channel 12 through the two channels is the same, so as to ensure that the lubricating oil can flow out from the first channel 151 and the second channel 161 at the same speed. In this way, it can be ensured that when the crankshaft rotates forward and backward at the same rotational speed, the lubricating oil supply amount supplied from the first spiral oil groove 13 is substantially equal to the lubricating oil supply amount supplied through the second spiral oil groove 14, so as to realize the equal oil supply of the crankshaft during forward and reverse equal-speed rotations, and avoid the problem of insufficient oil supply in one direction or excessive oil supply in the other direction under the condition of equal-speed rotation.

[0052] In another embodiment of the present invention, such as Figure 2 、 Figure 3 and Figure 4As shown, both the first channel 151 and the second channel 161 deflect and extend along the radial direction of the main shaft 10. In this way, the first channel 151 and the second channel 161 extend to communicate with the corresponding first oil hole 15 and second oil hole 16 with the minimum deflection length, reducing the resistance of the lubricating oil when flowing through the first channel 151 and the second channel 161, avoiding the phenomenon of water accumulation in the first channel 151 or the second channel 161, and ensuring that the lubricating oil can smoothly enter the distribution oil channel 12 at a certain flow rate.

[0053] In another embodiment of the present invention, please refer to Figure 2 and Figures 4 - 6 . In this embodiment, the first spiral oil groove 13 rotates a first rotation angle on the outer peripheral wall of the main shaft 10, and the second spiral oil groove 14 rotates a second rotation angle on the outer peripheral wall of the main shaft 10. Among them, as Figure 2 , Figure 4 and Figure 5 shown, the first rotation angle refers to: imagining the lubricating oil passing through the first spiral oil groove 13 as a mass point A' with a certain mass. The mass point A' flows from the first end of the first spiral oil groove 13 to the second end of the first spiral oil groove 13, that is, from the starting end to the ending end of the first spiral oil groove 13, and the angle of rotation around the outer peripheral wall of the main shaft 10, as shown by the included angle α in Figure 5 ; the second rotation angle refers to: imagining the lubricating oil passing through the second spiral oil groove 14 as a mass point A with a certain mass. The mass point A flows from the first end of the second spiral oil groove 14 to the second end of the second spiral oil groove 14, that is, from the starting end to the ending end of the second spiral oil groove 14, and the angle of rotation around the outer peripheral wall of the main shaft 10, as shown by the included angle β in Figure 5 .

[0054] Furthermore, in this embodiment, both the first rotation angle and the second rotation angle do not exceed 180°. Among them, when the maximum rotation angle of the first spiral oil groove 13 or the second spiral oil groove 14 around the main shaft 10 is 180°, the first end and the second end of the spiral oil groove are respectively located on the opposite side walls along the axial direction of the outer peripheral wall of the main shaft 10. At this time, as Figure 2 , Figure 4 and Figure 5 shown, when the second rotation angle is greater than the first rotation angle, the distribution oil channel 12 can be arranged close to the second channel 161, that is, the distribution oil channel 12 is arranged on the side of the main shaft 10 where the second channel 161 is provided, so that the second channel 161 extends to communicate with the first oil hole 15 with a shorter depth L2. On this basis, along the extension direction of the central axis of the main shaft 10, the distribution oil channel 12 is arranged to be offset towards the first channel 151, as Figure 2 shown, or the distribution oil channel 12 is arranged to be inclined towards the first channel 151, as Figure 4 and Figure 6As shown, the extending depth L1 of the first channel 151 is shortened, so as to ensure that the first channel 151 and the second channel 161 have substantially equal deflection depths, even if L1 is substantially equal to L2 in the figure, so that the amounts of lubricating oil flowing out through the first oil hole 15 and the second oil hole 16 are substantially equal.

[0055] In another embodiment of the present invention, as an alternative form of the above embodiment, in this embodiment, the distribution oil channel 12 can also be arranged at the central position of the main shaft 10 (not shown in the figure), that is, the central axis of the main shaft 10 passes through the center of the distribution oil channel 12, and the first spiral oil groove 13 and the second spiral oil groove 14 rotate the same rotation angle on the outer peripheral wall of the main shaft 10. In this way, the distance between the peripheral wall of the distribution oil channel 12 and the second end of the first spiral oil groove 13 is equal to the distance between the peripheral wall and the second end of the second spiral oil groove 14. In this way, the first channel 151 and the second channel 161 with the same deflection depth can be set, so that when the distribution oil channel 12 is arranged at the center of the main shaft 10, substantially equal oil supply during forward and reverse equal-speed rotation is also achieved.

[0056] In another embodiment of the present invention, please continue to refer to Figure 1 and Figure 2 The above-mentioned first spiral oil groove 13 and second spiral oil groove 14 can have the same pitch to further ensure that when the crankshaft rotates forward or backward and the rotational speeds are substantially equal, the amounts of lubricating oil supplied through the first spiral oil groove 13 and the second spiral oil groove 14 are also substantially equal, and the control of oil supply is more convenient.

[0057] It can be understood that the first spiral oil groove 13 and the second spiral oil groove 14 can also have different pitches. At this time, when the crankshaft has a higher rotational speed in a certain rotational direction, a greater amount of lubricating oil supply is required for the crankshaft in this rotational direction. In this way, by setting the pitches of the two spiral oil grooves to be different, the extending length of one of the two spiral oil grooves can be set longer to match the rotational speed of the crankshaft in this direction, so as to increase the supply amount of lubricating oil in the high rotational speed direction and avoid obvious excessive oil supply in the low rotational speed direction.

[0058] In another embodiment of the present invention, please continue to refer to Figure 1 and Figure 2 Near the bottom end of the main shaft 10, an oil inlet hole 17 is also provided. The oil inlet hole 17 penetrates the oil suction inner cavity 11, and the first spiral oil groove 13 and the second spiral oil groove 14 are communicated with the oil suction inner cavity 11 through the oil inlet hole 17. The lubricating oil in the oil suction inner cavity 11 can enter the first spiral oil groove 13 and the second spiral oil groove 14 through the oil inlet hole 17 under the pressure of the oil pump.

[0059] In some specific embodiments, such as Figure 1As shown, an oil inlet hole 17 can be provided on the main shaft 10. The two spiral oil grooves are communicated with the oil suction inner cavity 11 through the same oil inlet hole 17. In this way, only one oil inlet hole 17 is opened on the main shaft 10, reducing the processing and manufacturing steps of the main shaft 10, lowering the processing difficulty, and improving the production precision and efficiency of the main shaft 10.

[0060] In some other specific embodiments (not shown in the figure), two oil inlet holes 17 can also be provided on the main shaft 10. The two spiral oil grooves are communicated with the oil suction inner cavity 11 through different oil inlet holes 17. In this way, the two spiral oil grooves are independently communicated with the oil suction inner cavity 11, and the oil feeding processes do not affect each other. For some main shafts 10 with larger sizes, when the difficulty of processing two oil inlet holes 17 is relatively low, this design method can be considered.

[0061] In another embodiment of the present invention, please continue to refer to Figure 2 and Figure 3 to describe the setting positions of the outlets of the first channel 151 and the second channel 161 in the specific embodiment, that is, the first oil hole 15 and the second oil hole 16. In the specific embodiment of the present invention, the first oil hole 15 and the second oil hole 16 can be located at any position on the peripheral wall of the distribution oil channel 12, as long as it is ensured that the first channel 151 and the second channel 161 have substantially equal deflection depths.

[0062] In some specific embodiments, the first oil hole 15 and the second oil hole 16 are respectively located on opposite sides or adjacent sides of the peripheral wall of the distribution oil channel 12 (as Figure 2 shown), that is, on different sides of the peripheral wall of the distribution oil channel 12. At this time, the first spiral oil groove 13 and the second spiral oil groove 14 respectively enter the distribution oil channel 12 from different sides of the peripheral wall of the distribution oil channel 12. In this way, the first spiral oil groove 13 and the second spiral oil groove 14 can be arranged on opposite sides of the main shaft 10 along the radial direction of the main shaft 10 and can be arranged as symmetrically as possible on the outer peripheral wall of the main shaft 10. Since grooving on the outer peripheral wall of the main shaft 10 will affect the overall strength of the main shaft 10, therefore, arranging the two oil grooves symmetrically on both sides of the main shaft 10 can minimize the influence of the oil grooves on the overall strength of the main shaft 10.

[0063] In some other specific embodiments, the first oil hole 15 and the second oil hole 16 may also be located on the same side of the circumferential wall of the distribution oil passage 12. At this time, the extension length of one of the two oil grooves can be set longer. In this way, when the crankshaft has a higher rotational speed in a certain rotational direction, a larger lubricating oil supply amount is required by the crankshaft in this rotational direction. Correspondingly, setting the length of the oil groove consistent with this rotational direction longer can increase the lubricating oil supply amount in this direction. For example, in a specific embodiment, when the crankshaft rotates clockwise at a higher speed, the first spiral oil groove 13 is set longer than the second spiral oil groove 14. When the crankshaft rotates clockwise, the amount of lubricating oil supplied through the first spiral oil groove 13 is larger, which is more beneficial to the lubrication of the crankshaft and other rotating parts of the compressor using this crankshaft.

[0064] In another embodiment of the present invention, please refer to Figure 2 , Figure 5 and Figure 7 and 8 together. In this embodiment, the relative position relationship between the outlet of the first passage 151 and the outlet of the second passage 161 (i.e., the first oil hole 15 and the second oil hole 16) is further described. Among them, Figure 7 and Figure 8 are respectively schematic diagrams of the position relationships of the outlets of the first passage 151 and the second passage 161 of the main shaft 10 in different embodiments. As Figure 5 shown, taking the plane extending along the radial direction of the main shaft 10 as the projection plane, the central axis of the first passage 151 ( Figure 5 shown as Z1 in Figure 5 ) and the central axis of the second passage 161 (

[0065] shown as Z2 in Figure 7 ) have a projection angle θ in the projection plane, and θ satisfies 25° < θ < 155°. Figure 7 In this angular range, when two oil holes are arranged on the same side or adjacent sides of the circumferential wall of the distribution oil passage 12, as Figure 7 shown, it is ensured that on the axial direction of the main shaft 10 (as Figure 8 shown by the dashed line in Figure 8As shown by the dashed line, the two oil holes are offset from each other. When the crankshaft of this embodiment rotates at a high speed, lubricating oil flows out from the first oil hole 15 or the second oil hole 16. Most of the lubricating oil will be thrown out radially along the main shaft 10 under the action of centrifugal force, and will flow approximately along the Figure 7 direction indicated by the arrow in the figure, and the two oil holes are arranged offset radially along the main shaft 10 to prevent the lubricating oil flowing out radially from leaking again when rising along the channel wall of the distribution oil passage 12.

[0066] In some specific embodiments, the above-mentioned included angle θ can be 30°, 45°, 60°, 75°, 90°, 120°, 145°, etc., and can be selected according to needs in specific designs. The value of the included angle θ is not uniquely limited here.

[0067] In another embodiment of the present invention, please continue to refer to Figure 1 and Figure 2 In this embodiment, the heights of the outlets of the first hole passage 151 and the second hole passage 161 along the central axis direction of the main shaft 10 are the same or different, that is, the heights of the first oil hole 15 and the second oil hole 16 are the same or different. The same height setting means that the central axes of the first oil hole 15 and the second oil hole 16 are set at the same height. Different height settings mean that the top of the orifice of the first oil hole 15 is lower than the top of the orifice of the second oil hole 16, and the bottom of the orifice of the first oil hole 15 is lower than the bottom of the orifice of the second oil hole 16, that is, the first oil hole 15 and the second oil hole 16 are at least partially offset in the height direction.

[0068] In some specific embodiments, the top of the outlet of the second hole passage 161 (i.e., the top of the orifice of the second oil hole 16) can be set lower than the bottom of the outlet of the first hole passage 151 (i.e., the bottom of the orifice of the first oil hole 15), or the top of the outlet of the second hole passage 161 and the bottom of the outlet of the first hole passage 151 are located on the same straight line radially along the main shaft 10, that is, the first oil hole 15 and the second oil hole 16 are also completely offset in the axial direction of the main shaft 10, so as to further reduce the amount of lubricating oil leaking through the first oil hole 15 or the second oil hole 16 and better ensure the sufficient supply of lubricating oil.

[0069] In another embodiment of the present invention, please continue to refer to Figure 1 In this embodiment, the distribution oil passage 12 is set as a straight passage, and an oil outlet hole 31 is opened at the top of the crankshaft 30. The distribution oil passage 12 penetrates through the oil outlet hole 31, and the lubricating oil flows out from the top of the crankshaft 30 through the distribution oil passage 12 and finally reaches the inside of the compressor using the crankshaft of this embodiment, and effectively lubricates each rotating part.

[0070] In other embodiments of the present invention, please refer to Figure 9 , Figure 9Front view structure diagram of the crankshaft provided for another embodiment of the present invention. Some structures in the figure are perspective structures to illustrate the flow path of lubricating oil. In this embodiment, a section of the distribution oil passage 12 located on the main shaft 10 is a straight channel section 121, and a section of the distribution oil passage 12 located on the crankshaft 30 is an arc-shaped channel section 122 that bends away from the main shaft 10. An oil outlet hole 31 is opened on the side wall of the crankshaft 30, and the arc-shaped channel section 122 penetrates through the oil outlet hole 31. When the crankshaft rotates at a high speed, the oil outlet method of the lubricating oil flowing out from the top of the crankshaft may cause the oil outlet position to be too high, which is not convenient for lubricating components such as pistons that are set at a relatively low position in the compressor. Therefore, an oil outlet hole 31 is opened on the side wall of the crankshaft 30, and the distribution oil passage 12 is set as an arc-shaped channel that bends away from the main shaft 10 after entering the crankshaft 30, so that the lubricating oil flows out from the outer peripheral wall of the crankshaft 30 to better lubricate components such as pistons. Moreover, the arc-shaped channel structure that bends away from the main shaft 10 can make good use of the centrifugal force when the crankshaft 30 rotates, and the oil outflow of the lubricating oil is more guaranteed.

[0071] Of course, in some specific embodiments, the part of the distribution oil passage 12 located on the crankshaft 30 can be set in the form of a straight channel, and this straight channel part can be inclined relative to the central axis of the crankshaft 30.

[0072] The crankshafts of the above embodiments of the present invention can stably and reliably supply lubricating oil during forward and reverse rotations, and can also ensure sufficient lubricating oil supply during high-speed or low-speed rotations, so that the variable-frequency compressor using this crankshaft can operate efficiently and reliably under high-frequency and low-frequency working conditions. The variable-frequency operation of the variable-frequency compressor is more stable and more energy-saving.

[0073] Another embodiment of the present invention also provides a variable-frequency compressor, including the above-mentioned crankshaft.

[0074] The variable-frequency compressor provided by the embodiment of the present invention, by using the above-mentioned crankshaft, when the variable-frequency compressor of the present invention rotates at a constant speed in the forward and reverse directions, it can achieve equal supply of lubricating oil to ensure that the compressor can rotate at a constant speed and efficiently in the forward and reverse rotation directions, reduce the wear of the friction pair or reduce the waste of lubricating oil, ensure stable oil supply under different variable-frequency working conditions of the compressor, and the operation of the compressor is more stable and efficient. In addition, the variable-frequency compressor also has other technical effects of the crankshaft provided by the above embodiments, which will not be elaborated here.

[0075] Another embodiment of the present invention also provides a refrigeration device, which includes the above-mentioned variable-frequency compressor.

[0076] The refrigeration equipment provided by the embodiments of the present invention uses the variable-frequency compressors of the above embodiments, so that the operation of the refrigeration equipment is more stable, the refrigeration effect is more stable, the operation energy consumption is lower, and the service life is longer. In addition, the refrigeration equipment also has other technical effects of the variable-frequency compressors provided by the above embodiments, which will not be elaborated here.

[0077] In a specific embodiment, the above refrigeration equipment may be a refrigerator, an air conditioner, etc.

[0078] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A crankshaft, comprising a main shaft, a crankshaft and a crank, wherein the crankshaft is mounted at one end of the main shaft through the crank, and is characterized in that, One end of the main shaft away from the crankshaft is provided with an oil suction inner cavity. The other end of the main shaft connected to the crankshaft is provided with a distribution oil passage extending through the crankshaft. The outer wall surface of the main shaft is provided with a first spiral oil groove and a second spiral oil groove with opposite helix directions. One end of the first spiral oil groove and the second spiral oil groove is communicated with the oil suction inner cavity; The other end of the first spiral oil groove deflects towards the central axis of the main shaft and forms a first hole communicating with the distribution oil passage. The other end of the second spiral oil groove deflects towards the central axis of the main shaft and forms a second hole communicating with the distribution oil passage. The hole depth of the first hole is approximately equal to the hole depth of the second hole. The first hole and the second hole penetrate through the outer peripheral wall of the main shaft with approximately the same length and then communicate with the distribution oil passage, so that the resistance suffered by the lubricating oil when flowing through the first hole and the second hole is approximately equal. The area of the outlet of the first hole communicating with the distribution oil hole is approximately equal to the area of the outlet of the second hole communicating with the distribution oil hole, so that the outflow cross-sectional area of the outlet of the first hole communicating with the distribution oil passage is approximately equal to the outflow cross-sectional area of the outlet of the second hole communicating with the distribution oil passage; The setting height of the outlet of the first hole and the outlet of the second hole along the central axis direction of the main shaft is different.

2. The crankshaft according to claim 1, wherein, Both the first hole and the second hole extend along the radial direction of the main shaft.

3. The crankshaft according to claim 1, wherein The first spiral oil groove rotates a first rotation angle on the outer peripheral wall of the main shaft. The second spiral oil groove rotates a second rotation angle on the outer peripheral wall of the main shaft. Both the first rotation angle and the second rotation angle do not exceed 180°, and the second rotation angle is greater than the first rotation angle; wherein The distribution oil passage is arranged close to the second hole, and along the extending direction of the central axis of the main shaft, the distribution oil passage is offset or inclined towards the first hole.

4. The crankshaft according to claim 1, characterized in that, The distribution oil passage is arranged at the central position of the main shaft. The first spiral oil groove and the second spiral oil groove rotate approximately the same rotation angle on the outer peripheral wall of the main shaft.

5. The crankshaft according to any one of claims 1 to 4, characterized in that, The first spiral oil groove and the second spiral oil groove have the same pitch.

6. The crankshaft according to any one of claims 1 to 4, characterized in that, The setting height of the top of the outlet of the second hole is lower than or equal to the setting height of the bottom of the outlet of the first hole.

7. The crankshaft according to any one of claims 1 to 4, characterized in that, The main shaft is further provided with an oil inlet hole. The first spiral oil groove and the second spiral oil groove are communicated with the oil suction inner cavity through the oil inlet hole.

8. The crankshaft according to claim 7, characterized in that, The number of the oil inlet holes is one. The first spiral oil groove and the second spiral oil groove are communicated with the oil suction inner cavity through the same oil inlet hole; Or, the number of the oil inlet holes is two. The first spiral oil groove and the second spiral oil groove are respectively communicated with the oil suction inner cavity through two different oil inlet holes.

9. The crankshaft according to any one of claims 1 to 4, characterized in that, The distribution oil passage is a straight channel.

10. The crankshaft according to any one of claims 1 to 4, characterized in that, The section of the distribution oil passage located on the main shaft is a straight channel section, and the section of the distribution oil passage located at one end of the crankshaft is an arc-shaped channel section bent away from the main shaft.

11. A variable frequency compressor, characterized in that, Including the crankshaft according to any one of claims 1 to 10.

12. A refrigeration device, characterized in that: Including the variable frequency compressor according to claim 11.

Images