Compressor connecting rod, reciprocating compressor and refrigeration equipment

Abstract

The utility model provides a compressor connecting rod, a reciprocating compressor and refrigeration equipment, and belongs to the technical field of compressors, the compressor connecting rod comprises a rod body, two ends of the rod body along the length direction are respectively provided with a first head part and a second head part, and the first head part is provided with a first shaft hole for connecting a crankshaft; the second head is provided with a second shaft hole used for being connected with a piston, and the first shaft hole and the second shaft hole are coaxially arranged. An oil channel is formed in the rod body and penetrates through the rod body in the length direction of the rod body, a first oil groove formed in the circumferential direction of the first shaft hole is formed in the inner wall of the first shaft hole, a second oil groove formed in the circumferential direction of the second shaft hole is formed in the inner wall of the second shaft hole, and the first oil groove and the second oil groove communicate with the oil channel. The oil groove, the first oil duct and the second oil duct designed on the compressor connecting rod reduce the mass of the connecting rod, so that the inertia force of the connecting rod during movement is reduced, the unbalanced excitation of reciprocating movement is reduced, and the damping and noise reduction effects of the compressor are achieved.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a compressor connecting rod, a reciprocating compressor and a refrigeration device. Background Art

[0002] The unbalanced reciprocating inertial excitation of the crankshaft and connecting rod mechanism in the compressor is one of the main sources of vibration and noise. In the related art, the common method to reduce the reciprocating inertial excitation is to reduce the mass by optimizing the structural design of the crankshaft or piston, but no attention is paid to reducing the weight of the connecting rod. Utility Model Content

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, the utility model proposes a compressor connecting rod, which optimizes the structural design of the compressor connecting rod, reduces the mass of the connecting rod, thereby reducing the inertial force when the connecting rod moves, reduces the reciprocating inertial excitation of the connecting rod, and has a better effect of balancing the reciprocating inertial excitation.

[0004] The utility model also provides a reciprocating compressor with the compressor connecting rod.

[0005] The utility model also provides a refrigeration device having the reciprocating compressor.

[0006] According to the first aspect of the present invention, a compressor connecting rod includes:

[0007] A rod body, wherein the rod body is provided with a first head and a second head at both ends along the length direction thereof, the first head is provided with a first axial hole for connecting the crankshaft, the second head is provided with a second axial hole for connecting the piston, and the first axial hole and the second axial hole are coaxially arranged;

[0008] An oil passage is provided in the rod body, and the oil passage passes through the rod body along the length direction of the rod body. The inner wall of the first axial hole is provided with a first oil groove arranged along the circumference of the first axial hole, and the inner wall of the second axial hole is provided with a second oil groove arranged along the circumference of the second axial hole. The first oil groove and the second oil groove are respectively connected to the oil passage.

[0009] The compressor connecting rod according to the embodiment of the utility model has at least the following beneficial effects: the compressor connecting rod has a first head and a second head respectively provided at both ends of the rod body along its length direction, and the rod body is also provided with an oil passage along its length direction, the first head is connected to the crankshaft through a first axial hole, and a first oil groove is provided on the inner wall of the first axial hole, the second head is connected to the piston through a second axial hole, and a second oil groove is provided on the inner wall of the second axial hole, the first oil groove and the second oil groove are both connected to the oil passage, the first oil groove is used to transport lubricating oil to the connection part between the compressor connecting rod and the crankshaft, and the second oil groove is used to transport lubricating oil to the connection part between the compressor connecting rod and the piston; in addition, adding the first oil groove is beneficial to reducing the mass of the first head, and adding the second oil groove is beneficial to reducing the mass of the second head, and the oil passage reduces the mass of the rod body, thereby reducing the overall mass of the compressor connecting rod, reducing the inertia force of the compressor connecting rod during movement, reducing the unbalanced excitation of the reciprocating motion of the compressor connecting rod, and achieving the effect of shock absorption and noise reduction.

[0010] According to some embodiments of the present invention, the maximum width of the first oil groove along the axial direction of the first shaft hole is smaller than the maximum diameter of the oil channel, and the maximum width of the second oil groove along the axial direction of the second shaft hole is smaller than the maximum diameter of the oil channel.

[0011] According to some embodiments of the present invention, a maximum width of the first oil groove along the axial direction of the first shaft hole ranges from 0.8 mm to 1.4 mm, and a maximum depth of the first oil groove ranges from 0.4 mm to 1 mm.

[0012] According to some embodiments of the present invention, a maximum width of the second oil groove along the axial direction of the second shaft hole ranges from 0.6 mm to 1.2 mm, and a maximum depth of the second oil groove ranges from 0.4 mm to 1 mm.

[0013] According to some embodiments of the present invention, the maximum diameter of the oil channel ranges from 1.2 mm to 2.5 mm.

[0014] According to some embodiments of the utility model, an oil hole is provided on a side of the second head away from the rod body, and a third oil groove is provided on the outer wall of the second head. The third oil groove is arranged along the axial direction of the second shaft hole, and the third oil groove is connected with the second oil groove through the oil hole.

[0015] According to some embodiments of the utility model, the cross-section of the rod body is square, and the outer wall of the rod body is provided with at least two weight-reducing grooves, and the at least two weight-reducing grooves are distributed on at least two opposite wall surfaces of the rod body.

[0016] According to some embodiments of the utility model, the weight-reducing groove is arranged along the length direction of the rod body, the maximum width range of the weight-reducing groove is 4 mm to 5 mm, and the maximum depth range of the weight-reducing groove is 1 mm to 2 mm.

[0017] A reciprocating compressor according to a second aspect of the present invention includes:

[0018] A crankcase having mounting holes and cylinder bores;

[0019] A crankshaft, comprising a main shaft and a secondary shaft eccentrically arranged with respect to the main shaft, wherein the main shaft is rotatably connected to the mounting hole;

[0020] A piston disposed in the cylinder hole;

[0021] As for the compressor connecting rod described in the first embodiment, the first shaft hole is connected to the secondary shaft, and the second shaft hole is connected to the piston.

[0022] The reciprocating compressor according to the embodiment of the utility model has at least the following beneficial effects: the reciprocating compressor adopts the compressor connecting rod of the above embodiment, and adding the first oil groove on the compressor connecting rod is beneficial to reducing the mass of the first head, and adding the second oil groove is beneficial to reducing the mass of the second head, and the oil channel reduces the mass of the rod body, thereby reducing the overall mass of the compressor connecting rod, reducing the inertial force of the compressor connecting rod during movement, reducing the unbalanced excitation of the reciprocating motion of the compressor connecting rod, achieving the effect of shock absorption and noise reduction, and effectively reducing the noise of the reciprocating compressor.

[0023] A refrigeration device according to a third aspect of the present invention includes:

[0024] A reciprocating compressor as described in the second embodiment.

[0025] Since the refrigeration equipment has all the technical solutions of the compressor connecting rod of the first embodiment and the reciprocating compressor of the second embodiment, the refrigeration equipment has at least all the above-mentioned beneficial effects, which will not be repeated here. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 This is a partial structural exploded diagram of a compressor according to an embodiment of the utility model;

[0027] Figure 2 It is a schematic diagram of a compressor connecting rod according to an embodiment of the utility model;

[0028] Figure 3 yes Figure 2 A top view of a compressor connecting rod is shown;

[0029] Figure 4 yes Figure 3 A cross-sectional view taken along line AA of a compressor connecting rod is shown;

[0030] Figure 5 yes Figure 2A front view of a compressor connecting rod is shown;

[0031] Figure 6 for Figure 5 A cross-sectional view of the BB of a compressor connecting rod is shown.

[0032] Reference numerals:

[0033] Compressor connecting rod 100;

[0034] Rod body 110, oil passage 111, weight reduction groove 112, first head 120, first shaft hole 121, first oil groove 1210, second head 130, second shaft hole 131, second oil groove 1310, oil hole 140, third oil groove 150;

[0035] Crankcase 200, mounting hole 210, cylinder hole 220;

[0036] Crankshaft 300, main shaft 310, secondary shaft 320, crank arm 330, balance block 340;

[0037] Piston 400 and connecting shaft 410 . DETAILED DESCRIPTION

[0038] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0039] In the description of the present invention, it should be understood that descriptions involving orientation, such as up, down, front, back, left, right, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply 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 on the present invention.

[0040] In the description of the present utility model, "several" means one or more, "more" means more than two, "greater than", "less than", "exceed" etc. are understood to exclude the number itself, and "above", "below", "within" etc. are understood to include the number itself. If there is a description of "first" or "second", it is only used for the purpose of distinguishing the technical features, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0041] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0042] As a core component of the refrigerator, the refrigerator compressor compresses the refrigerant, thereby promoting the refrigerant to circulate in the refrigerator's refrigeration system to achieve the refrigerator's refrigeration effect. The compressor determines the noise, vibration and harshness (NVH) level of the entire refrigerator. In a reciprocating compressor, the crankshaft connecting rod mechanism is the main undertaker of converting rotational motion into reciprocating motion in the reciprocating compressor. The crank-connecting rod mechanism includes a crank, a connecting rod, a piston and related connection and installation parts. The crank has a main shaft and a secondary shaft eccentrically arranged with the main shaft. The main shaft and the secondary shaft are connected by a crank arm. One end of the connecting rod is arranged on the secondary shaft, and the piston is arranged at the end of the connecting rod away from the secondary shaft.

[0043] In the related art, the inertial excitation of the reciprocating motion of the crank-connecting rod mechanism of the compressor is reduced by optimizing the structural design of the crankshaft or the piston to reduce the mass. Specifically, the crank arm of the crankshaft is designed to reduce weight, such as by digging grooves or designing through holes, notches, etc.; or the piston is designed to reduce weight, such as by digging grooves, etc. However, in these improvements, no attention is paid to the weight reduction design of the connecting rod.

[0044] In view of the above technical problems, according to the embodiment of the first aspect of the utility model, a compressor connecting rod is proposed, and according to the embodiment of the second aspect of the utility model, a reciprocating compressor having the compressor connecting rod is proposed. By optimizing the structural design of the connecting rod, the unbalanced excitation of the reciprocating motion of the crank-connecting rod mechanism of the compressor is reduced, and the influence of the reciprocating compressor on the overall NVH level of the refrigerator is effectively reduced. Specific embodiments are listed below for illustration.

[0045] Reference Figure 1 As shown, the reciprocating compressor includes a compressor connecting rod 100, a crankcase 200, a crankshaft 300 and a piston 400, wherein the crankcase 200 is provided with a mounting hole 210 and a cylinder hole 220, the crankshaft 300 includes a main shaft 310, a secondary shaft 320 and a crank arm 330, the main shaft 310 and the secondary shaft 320 are respectively arranged at both ends of the crank arm 330, and the main shaft 310 and the secondary shaft 320 are eccentrically arranged, the main shaft 310 is rotatably connected to the mounting hole 210, the piston 400 is movably arranged in the cylinder hole 220, and the compressor connecting rod 100 connects the secondary shaft 320 of the crankshaft 300 and the piston 400. The crankshaft 300 is provided with a channel for conveying lubricating oil, and the lubricating oil can flow from one end of the main shaft 310 to the outer peripheral wall of the secondary shaft 320 through the above-mentioned channel for conveying lubricating oil.

[0046] It is understandable that when the crankshaft 300 rotates, the secondary shaft 320 of the crankshaft 300 rotates around the main shaft 310, one end of the compressor connecting rod 100 moves with the secondary shaft 320, and the other end drives the piston 400 to move, so that the piston 400 performs a linear reciprocating motion in the cylinder bore 220.

[0047] It should be noted that the crank arm 330 is also provided with a balancing block 340, and the position of the balancing block 340 is symmetrical to the position of the secondary shaft 320, that is, the balancing block 340 and the secondary shaft 320 are respectively located on both sides of the center of the crank arm 330, and the balancing block 340 can balance the rotational mass of the crank arm 330 and the secondary shaft 320, wherein the rotational mass refers to the mass distribution of an object in rotational motion. The balancing block 340 is provided to reduce the rotational mass of the crank arm 330 and the secondary shaft 320, which can effectively reduce the inertia force generated when the crank arm 330 and the secondary shaft 320 rotate, thereby improving the stability of the crankshaft connecting rod mechanism and reducing vibration.

[0048] Reference Figure 2 As shown, the compressor connecting rod 100 includes a rod body 110, and the rod body 110 is provided with a first head 120 and a second head 130 at both ends along the length direction thereof, the first head 120 is used to connect the crankshaft 300 in the crank-connecting rod mechanism, and the second head 130 is used to connect the piston 400 in the crank-connecting rod mechanism. The first head 120 is provided with a first shaft hole 121, the first shaft hole 121 is connected to the secondary shaft 320 of the crankshaft 300, and the second head 130 is provided with a second shaft hole 131, and the second shaft hole 131 is connected to the connecting shaft 410 of the piston 400. The secondary shaft 320 of the crankshaft 300 can rotate in the first shaft hole 121, and the connecting shaft 410 of the piston 400 can rotate in the second shaft hole 131. Since the torque borne by the secondary shaft 320 of the crankshaft 300 is greater than that of the connecting shaft 410 of the piston 400, the size of the secondary shaft 320 of the crankshaft 300 is larger than that of the connecting shaft 410 of the piston 400, and the inner diameter of the first shaft hole 121 is designed to be larger than the inner diameter of the second shaft hole 131.

[0049] Reference Figure 4 and Figure 6As shown, an oil passage 111 is provided in the rod body 110, and the oil passage 111 penetrates the rod body 110 along the length direction of the rod body 110, and a first oil groove 1210 is provided on the inner wall of the first shaft hole 121 along the circumference of the first shaft hole 121, and a second oil groove 1310 is provided on the inner wall of the second shaft hole 131 along the circumference of the second shaft hole 131, and the first oil groove 1210 and the second oil groove 1310 are respectively connected to the oil passage 111. It should be noted that the oil passage 111 coincides with the axis of the rod body 110, and the mass distribution of the rod body 110 is uniform, so that the rod body 110 is uniformly stressed during operation, and it is ensured that the oil passage 111 will not affect the fatigue strength of the rod body 110. The first oil groove 1210 is located at the middle position of the inner wall of the first shaft hole 121 along the axis direction thereof, and similarly, the second oil groove 1310 is located at the middle position of the inner wall of the second shaft hole 131 along the axis direction thereof. After the secondary shaft 320 of the crankshaft 300 is installed in the first shaft hole 121 of the rod body 110, the oil outlet hole of the secondary shaft 320 for outputting lubricating oil is connected to the first oil groove 1210, and the lubricating oil output by the secondary shaft 320 flows into the oil channel 111 of the rod body 110 through the first oil groove 1210, and then flows into the second oil groove 1310.

[0050] It can be understood that when the crank-connecting rod mechanism is working, the crankshaft 300 rotates, and the lubricating oil enters the main shaft 310 of the crankshaft 300 under the action of negative pressure and reaches the secondary shaft 320 through the channel for conveying the lubricating oil, and then enters the first oil groove 1210 through the oil outlet hole. Part of the lubricating oil flows from the first oil groove 1210 to the inner wall of the first shaft hole 121, and another part of the lubricating oil flows from the first oil groove 1210 into the oil channel 111 of the rod body 110, and then flows through the oil channel 111 of the rod body 110 to the second oil groove 1310, and flows out from the second oil groove 1310 to the inner wall of the second shaft hole 131, thereby realizing the lubrication of the crankshaft 300, the compressor connecting rod 100 and the piston 400.

[0051] The first oil groove 1210 and the second oil groove 1310 are provided to reduce the mass of the compressor connecting rod 100, that is, the mass of the first head 120 and the second head 130 are both reduced, thereby reducing the rotational mass of the compressor connecting rod 100 and the secondary shaft 320, and reducing the rotational mass of the compressor connecting rod 100 and the piston 400, thereby reducing the rotational mass of the crank-connecting rod mechanism, reducing the inertial force generated when the crankshaft 300, the compressor connecting rod 100 and the piston 400 and their related connecting and mounting components rotate, and effectively reducing the reciprocating inertial excitation of the crank-connecting rod mechanism of the reciprocating compressor, and achieving a good effect of balancing the reciprocating inertial excitation.

[0052] The second function of the first oil groove 1210 and the second oil groove 1310 is to increase the flow rate of the lubricating oil in the oil delivery path of the compressor connecting rod 100, improve the lubrication effect, and further reduce the friction between the compressor connecting rod 100 and the secondary shaft 320 of the crankshaft 300, and between the compressor connecting rod 100 and the piston 400. Specifically, the lubricating oil flowing from the crankshaft 300 to the first head 120 of the compressor connecting rod 100 can enter the oil passage 111 more from the first oil groove 1210, and the amount of lubricating oil input to the first head 120 is increased; the lubricating oil flowing from the oil passage 111 to the second head 130 of the compressor connecting rod 100 can enter the second oil groove 1310 more, and the amount of lubricating oil input to the second head 130 is increased, thereby reducing the friction between the first head 120 and the secondary shaft 320 of the crankshaft 300, and reducing the friction between the second head 130 and the piston 400, so that the compressor runs more smoothly, which can not only reduce the energy consumption of the compressor, but also increase the service life of the compressor and reduce the loss.

[0053] In addition, the first oil groove 1210 is located in the middle position of the first shaft hole 121, which can increase the amount of lubricating oil input from the first oil groove 1210 to the inner wall of the first shaft hole 121. The lubricating oil in the first oil groove 1210 can flow from both sides of the first oil groove 1210 to the inner wall of the first shaft hole 121, and the inner wall of the first shaft hole 121 is separated by the first oil groove 1210 to form two wall surfaces, and the areas of the two wall surfaces are the same, that is, the time for the lubricating oil to flow from the first oil groove 1210 to the wall surfaces on both sides of the first oil groove 1210 is similar, which effectively increases the amount of lubricating oil input and increases the inner wall of the first shaft hole 121. Similarly, the second oil groove 1310 is located in the middle position of the second shaft hole 131, which can increase the amount of lubricating oil output from the second oil groove 1310 to the inner wall of the second shaft hole 131, and the lubricating oil in the second oil groove 1310 can flow from both sides of the second oil groove 1310 to the inner wall of the second shaft hole 131, and the inner wall of the second shaft hole 131 is separated by the second oil groove 1310 to form two wall surfaces, and the areas of the two wall surfaces are the same, that is, the time for the lubricating oil to flow from the second oil groove 1310 to the walls on both sides of the second shaft hole 131 is similar, which effectively enhances the lubrication effect of the second shaft hole 131.

[0054] It should be noted that the position of the first oil groove 1210 relative to the first axial hole 121 and the position of the second oil groove 1310 relative to the second axial hole 131 are not limited to the above-mentioned position arrangement. In other embodiments, the first oil groove 1210 and the second oil groove 1310 can also be arranged at an angle.

[0055] Reference Figure 4 and Figure 6As shown, the maximum width of the first oil groove 1210 along the axial direction of the first shaft hole 121 is smaller than the maximum diameter of the oil passage 111, and the maximum width of the second oil groove 1310 along the axial direction of the second shaft hole 131 is also smaller than the maximum diameter of the oil passage 111. It can be understood that after the lubricating oil flows out from the oil outlet hole of the secondary shaft 320, it will enter the oil passage 111 and the first oil groove 1210. The lubricating oil in the first oil groove 1210 has a high oil pressure and a faster flow rate, while the oil pressure in the oil passage 111 is low and the flow rate is slow. The oil passage 111 plays the role of temporarily storing the lubricating oil, reducing the overflow of the lubricating oil; the lubricating oil flows from the oil passage 111 into the second oil groove 1310, the oil pressure increases, the flow rate accelerates, and the inner wall of the second shaft hole 131 can be quickly lubricated, thereby improving the lubrication efficiency. If the diameter of the oil passage 111 is smaller than the width of the first oil groove 1210 and the second oil groove 1310 , not only the amount of lubricating oil entering the oil passage 111 is reduced, but also the amount of lubricating oil entering the second oil groove 1310 is reduced, thereby affecting the lubrication effect of the second head 130 and the piston 400 .

[0056] It should be noted that, in the embodiment provided by the present utility model, the maximum width L of the first oil groove 1210 along the axial direction of the first shaft hole 121 is 1 The maximum depth range of the first oil groove 1210 is H 1 After repeated tests and accumulated experience, the maximum width L of the first oil groove 1210 along the axial direction of the first shaft hole 121 is 1 The maximum depth H of the first oil groove 1210 is in the range of 0.8 mm to 1.4 mm. 1 When the range is between 0.4 mm and 1 mm, the fatigue strength of the first head 120 of the compressor connecting rod 100 is not affected by the first oil groove 1210, and the lubricating oil in the first oil groove 1210 is subjected to a small viscous force and a stable flow rate. For example, the maximum width L of the first oil groove 1210 is 1 It can be set to 0.8 mm, 1 mm, 1.4 mm, etc. The maximum depth H of the first oil groove 1210 1 It can be set to 0.4mm, 0.8mm, 1mm, etc. The maximum width L of the first oil groove 1210 1 and the maximum depth H 1 The specific value of can be selected according to the actual application requirements.

[0057] When the maximum width L of the first oil groove 1210 along the axial direction of the first shaft hole 121 is 1 Less than 0.8 mm, the maximum depth H of the first oil groove 1210 1When the maximum width L of the first oil groove 1210 along the axial direction of the first shaft hole 121 is less than 0.4 mm, the viscosity of the lubricating oil in the first oil groove 1210 increases, the flow of the lubricating oil is not smooth, the delivery effect of the lubricating oil is affected, and the weight reduction effect on the compressor connecting rod 100 is not obvious. 1 Greater than 1.4 mm, the maximum depth H of the first oil groove 1210 1 When it is larger than 1 mm, it is easy to cause waste of lubricating oil, accelerate the consumption of lubricating oil, and affect the structural rigidity of the first head 120, reducing its fatigue strength.

[0058] Similarly, in the embodiment provided by the present utility model, the maximum width L of the second oil groove 1310 along the axial direction of the second shaft hole 131 is 2 The maximum depth range of the second oil groove 1310 is H 2 After repeated tests and accumulated experience, the maximum width L of the second oil groove 1310 along the axial direction of the second shaft hole 131 is 2 The maximum depth H of the second oil groove 1310 is in the range of 0.6 mm to 1.2 mm. 2 When the range is between 0.4 mm and 1 mm, the fatigue strength of the big end of the compressor connecting rod 100 is not affected by the first oil groove 1210, and the lubricating oil in the first oil groove 1210 is subjected to a small viscous force and a stable flow rate. For example, the maximum width L of the second oil groove 1310 is 2 It can be set to 0.6mm, 1mm, 1.2mm, etc. The maximum depth H of the second oil groove 1310 2 It can be set to 0.4mm, 0.8mm, 1mm, etc. The maximum width L of the second oil groove 1310 is 2 and the maximum depth H 2 The specific value of can be selected according to the actual application requirements. The maximum width L of the second oil groove 1310 along the axial direction of the second shaft hole 131 2 The maximum depth H of the second oil groove 1310 is outside the range of 0.6 mm to 1.2 mm. 2 The disadvantages outside the range of 0.4 mm to 1 mm are similar to those of the first oil groove 1210 , and will also affect the fluidity of the lubricating oil in the second oil groove 1310 and the structural rigidity of the second head 130 , which will not be described in detail here.

[0059] It is understood that, in some embodiments, the width of the first oil groove 1210 along the axial direction of the first shaft hole 121 is greater than the width of the second oil groove 1310 along the axial direction of the second shaft hole 131. The lubricating oil enters the first oil groove 1210 first. Since the path through which it passes is shorter, the oil pressure in the first oil groove 1210 is greater. The width of the first oil groove 1210 can be designed to be relatively large. Then, after the lubricating oil passes through the oil passage 111, the oil pressure will decrease due to the increase in the path. The width of the second oil groove 1310 is designed to be smaller than the width of the first oil groove 1210, which can increase the oil pressure of the lubricating oil entering the second oil groove 1310, and is conducive to the input of the lubricating oil into the second oil groove 1310 and lubrication of the inner wall of the second shaft hole 131. It should be noted that, in other embodiments, the width of the first oil groove 1210 can also be designed to be the same as the width of the second oil groove 1310.

[0060] Reference Figure 4 and Figure 6 As shown, the maximum diameter R of the oil passage 111 ranges from 1.2 mm to 2.5 mm. After repeated tests and accumulated experience, it is found that the design of the oil passage 111 will not affect the fatigue strength of the compressor connecting rod 100. The diameter of the oil passage 111 is designed to be larger than the width of the first oil groove 1210 and larger than the width of the second oil groove 1310, which can make the oil pressure in the oil passage 111 smaller. The oil passage 111 achieves the purpose of temporary lubrication and reduces the consumption of lubricating oil. The maximum diameter R of the oil passage 111 can be set to 1.2 mm, 1.5 mm, 2 mm, etc. The specific value of the maximum diameter R of the oil passage 111 can be selected according to the actual application requirements.

[0061] It is understandable that when the maximum diameter R range of the oil channel 111 is less than 1.2 mm, the viscosity of the lubricating oil in the oil channel 111 will increase and the fluidity of the lubricating oil will deteriorate. When the maximum diameter R range of the oil channel 111 is greater than 2.5 mm, it will affect the structural rigidity of the rod body 110 and reduce fatigue strength.

[0062] Reference Figure 2 and Figure 4 As shown, an oil hole 140 is provided on a side of the second head 130 of the compressor connecting rod 100 away from the rod body 110, and the oil hole 140 penetrates the inner wall and the outer wall of the second head 130. A third oil groove 150 is provided on the outer wall of the second head 130, and the third oil groove 150 is arranged along the axial direction of the second shaft hole 131. The third oil groove 150 is connected with the second oil groove 1310 through the oil hole 140. It should be noted that the direction of the oil hole 140 is parallel to the length direction of the oil passage 111, and the third oil groove 150 is parallel to the axis of the second shaft hole 131.

[0063] It is understandable that the lubricating oil in the second oil groove 1310 can flow to the outer peripheral wall of the second head 130 through the oil hole 140, and then flow to the inner wall of the piston 400 to lubricate the connecting shaft 410 of the piston 400. The first function of the third oil groove 150 is to speed up the flow of the lubricating oil to the outer peripheral wall of the second head 130 and improve the lubrication efficiency; the second function is to further reduce the mass of the second head 130, thereby reducing the balanced reciprocating inertial excitation when the connecting rod rotates.

[0064] It should be noted that, in other embodiments, the third oil groove 150 may also be a structure circumferentially arranged around the outer wall of the second head 130 .

[0065] Reference Figure 5 and Figure 6 In some embodiments, the rod body 110 is square, and the rod body 110 is provided with two weight-reducing grooves 112, which are respectively located on two opposite sides of the rod body 110. By adding the weight-reducing grooves 112, the mass of the rod body 110 can be further reduced, thereby reducing the rotational mass of the compressor connecting rod 100, effectively reducing the reciprocating inertial force, and facilitating the reduction of the reciprocating inertial excitation, so that the crank-connecting rod mechanism can achieve a better balance effect.

[0066] The arrangement of the weight-reducing groove 112 makes the cross section of the rod body 110 an I-shaped structure. The rod body 110 of this structure has a higher structural strength, so that the influence of the oil passage 111 arranged on the rod body 110 on the structural rigidity is further reduced.

[0067] It should be noted that the weight-reducing groove 112 is arranged along the length direction of the rod body 110, and the maximum width L of the weight-reducing groove 112 is 3 The maximum depth H of the weight-reducing groove 112 is 4 mm to 5 mm. 3 The range is 1mm to 2mm. After repeated tests and accumulated experience, the weight reduction groove 112 is designed as above to reduce the mass as much as possible under the premise of having a high fatigue strength of the rod body 110, realize the lightweight design of the rod body 110, and reduce the inertia force generated by the rotation of the rod body 110. For example, the maximum width L of the weight reduction groove 112 is 3 It can be set to 4mm, 4.5mm, 5mm, etc. The maximum depth H 3 It can be set to 1mm, 1.5mm, 2mm, etc. The specific value can be selected according to the actual application requirements. In addition, the number of weight reduction grooves 112 is not limited to two. In some embodiments, four weight reduction grooves 112 can be provided. The four weight reduction grooves 112 are respectively provided on the four side walls of the rod body 110, which can further reduce the mass of the rod body 110.

[0068] It should be noted that according to the formula F = mrω 2, where F represents the rotational inertia force, m represents the mass of the compressor connecting rod 100, r represents the distance from the mass center to the rotation center, and ω represents the angular velocity of the mass center. When the mass of the compressor connecting rod 100 is designed to be smaller, its rotational inertia force will be reduced accordingly, effectively reducing the reciprocating inertial excitation of the connecting rod.

[0069] According to the third aspect, a refrigeration device is provided, which has a reciprocating compressor of the second aspect. Since the refrigeration device has all the technical solutions of the compressor, the refrigeration device has at least all the beneficial effects of the above embodiments. The inertial excitation of the reciprocating motion of the crank-connecting rod mechanism is reduced, the effect of balancing the reciprocating inertial excitation is good, and the NVH level of the refrigeration device is improved.

[0070] It is understandable that the refrigeration equipment may specifically be an appliance such as a refrigerator or a freezer. Taking a refrigerator as an example, the refrigerator uses the reciprocating compressor of the above embodiment to improve the NVH level of the refrigerator, with small vibration and low noise, thus achieving an effective noise reduction effect.

[0071] The embodiments of the present invention are described in detail above in conjunction with the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A compressor connecting rod, applied to a compressor having a crankshaft and a piston, characterized in that: include: A rod body, wherein the rod body is provided with a first head and a second head at both ends along the length direction thereof, the first head is provided with a first axial hole for connecting the crankshaft, the second head is provided with a second axial hole for connecting the piston, and the first axial hole and the second axial hole are coaxially arranged; An oil passage is provided in the rod body, and the oil passage passes through the rod body along the length direction of the rod body. The inner wall of the first axial hole is provided with a first oil groove arranged along the circumference of the first axial hole, and the inner wall of the second axial hole is provided with a second oil groove arranged along the circumference of the second axial hole. The first oil groove and the second oil groove are respectively connected to the oil passage.

2. The compressor connecting rod according to claim 1, characterized in that: The maximum width of the first oil groove along the axial direction of the first shaft hole is smaller than the maximum diameter of the oil passage, and the maximum width of the second oil groove along the axial direction of the second shaft hole is smaller than the maximum diameter of the oil passage.

3. The compressor connecting rod according to claim 1 or 2, characterized in that: The maximum width of the first oil groove along the axial direction of the first shaft hole ranges from 0.8 mm to 1.4 mm, and the maximum depth of the first oil groove ranges from 0.4 mm to 1 mm.

4. The compressor connecting rod according to claim 1 or 2, characterized in that: The maximum width of the second oil groove along the axial direction of the second shaft hole ranges from 0.6 mm to 1.2 mm, and the maximum depth of the second oil groove ranges from 0.4 mm to 1 mm.

5. The compressor connecting rod according to claim 1 or 2, characterized in that: The maximum diameter of the oil channel ranges from 1.2 mm to 2.5 mm.

6. The compressor connecting rod according to claim 1, characterized in that: An oil hole is provided on a side of the second head away from the rod body, and a third oil groove is provided on an outer wall of the second head. The third oil groove is arranged along the axial direction of the second shaft hole, and the third oil groove is connected with the second oil groove through the oil hole.

7. The compressor connecting rod according to claim 1, characterized in that: The cross section of the rod body is square, and the outer wall of the rod body is provided with at least two weight-reducing grooves, and the at least two weight-reducing grooves are distributed on at least two opposite wall surfaces of the rod body.

8. The compressor connecting rod according to claim 7, characterized in that: The weight-reducing groove is arranged along the length direction of the rod body, the maximum width range of the weight-reducing groove is 4 mm to 5 mm, and the maximum depth range of the weight-reducing groove is 1 mm to 2 mm.

9. A reciprocating compressor, characterized in that: include: A crankcase having mounting holes and cylinder bores; A crankshaft, comprising a main shaft and a secondary shaft eccentrically arranged with respect to the main shaft, wherein the main shaft is rotatably connected to the mounting hole; A piston disposed in the cylinder hole; The compressor connecting rod according to any one of claims 1 to 8, wherein the first axial hole is connected to the secondary shaft, and the second axial hole is connected to the piston.

10. A refrigeration device, characterized in that: A reciprocating compressor comprising the method of claim 9.

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