A crankshaft piston assembly, variable frequency rolling single rotor compressor and air conditioner

Abstract

The application discloses a crankshaft piston assembly, a variable-frequency rolling single-rotor compressor and an air conditioner, which comprises a crankshaft body and a piston body; an eccentric part is arranged on the crankshaft body, and the piston body is arranged on the outer circle of the eccentric part; a first annular groove is arranged on the outer circle of the eccentric part, and the eccentric part is divided into an upper eccentric section and a lower eccentric section; the first annular groove is located in the middle of the eccentric part; a second annular groove is arranged on the inner hole wall of the piston body, and the inner hole wall of the piston body is divided into an upper hole wall section and a lower hole wall section; the second annular groove is located in the middle of the inner hole wall of the piston body; the upper eccentric section is matched with the upper hole wall section, and the lower eccentric section is matched with the lower hole wall section; the application effectively reduces the centrifugal inertia force and the inertia moment of the eccentric part and the piston, thereby effectively reducing the mass of the balance weight block of the motor rotor and further reducing the air resistance; meanwhile, the friction power consumption between the eccentric part and the piston is reduced, and the operation power of the compressor is effectively improved.

Description

TECHNICAL FIELD

[0001] The present application belongs to the technical field of compressors, in particular to a crankshaft piston assembly, a variable frequency rolling single rotor compressor and an air conditioner. BACKGROUND

[0002] At present, the 2HP and above compressors for variable frequency air conditioners generally adopt a double rotor structure; wherein, two eccentric parts of the crankshaft are arranged at 180° relative to each other, and two rolling pistons installed on the eccentric parts work simultaneously with a 180° rotation angle difference; the symmetrical structure in the double rotor compressor balances its own rotational inertia force, and it only needs to balance the rotational inertia moment generated by the two eccentric masses not in the same plane; wherein, the balance weight mass of the motor is small and the height is low, and the running wind resistance generated by the balance weight is small, so the whole machine vibration is low.

[0003] With the development of compressor technology, the 2HP and above compressors gradually change from a double rotor structure to a single rotor structure; compared with a 1HP compressor, the cylinder and piston height of a 2HP and above single rotor compressor increases, which increases the contact area between the eccentric part of the crankshaft and the inner hole of the piston, and the friction power consumption between them increases; for example, when the cylinder inner diameter is 43mm and the crankshaft eccentric distance is unchanged, the height of the cylinder and the piston needs to be increased by 31%; at the same time, in the single rotor compressor, due to the eccentric rotation characteristics of the eccentric part and the piston; therefore, the centrifugal inertia force generated during the operation of the compressor cannot be balanced itself, and needs to be offset by the balance weight at both ends of the motor rotor; on the one hand, the unbalanced force of the balance weight is increased due to the increase of the height of the eccentric part and the piston, and on the other hand, the centrifugal inertia force of the eccentric part and the piston needs to be offset, which makes the balance weight much larger in mass and higher in height compared with the double rotor, and further increases the wind resistance of the balance weight during the operation of the compressor, causing the whole machine vibration and power deterioration. SUMMARY

[0004] In view of the technical problems existing in the prior art, the present application provides a crankshaft piston assembly, a variable frequency rolling single rotor compressor and an air conditioner, to solve the technical problems that the cylinder and piston height of the existing 2HP and above single rotor compressor increases, which increases the contact area between the eccentric part of the crankshaft and the inner hole of the piston, and the friction power consumption between them increases; at the same time, the wind resistance of the balance weight increases during the operation of the compressor, causing the whole machine vibration and power deterioration.

[0005] To achieve the above-mentioned purpose, the technical scheme adopted by the present application is as follows:

[0006] The present application provides a crankshaft piston assembly, comprising a crankshaft body and a piston body; an eccentric part is arranged on the crankshaft body, and the piston body is sleeved on the outer circle of the eccentric part;

[0007] The outer circle of the eccentric part is provided with a first annular groove, which divides the eccentric part into an upper eccentric section and a lower eccentric section; wherein the first annular groove is located in the middle of the eccentric part and extends along the axial direction of the eccentric part;

[0008] The inner hole wall of the piston body is provided with a second annular groove, which divides the inner hole wall of the piston body into an upper hole wall section and a lower hole wall section; wherein the second annular groove is located in the middle of the inner hole wall of the piston body and extends along the axial direction of the piston body; the upper eccentric section cooperates with the upper hole wall section, and the lower eccentric section cooperates with the lower hole wall section.

[0009] Further, the first annular groove is symmetrically distributed along the axial center section of the outer circle of the eccentric part, and the center line of the first annular groove coincides with the rotation center axis of the crankshaft body.

[0010] Further, the axial extension length w of the first annular groove satisfies: 0.1≤w / b≤0.6; wherein b is the total length of the eccentric part in the axial direction; the axial extension length W of the second annular groove satisfies: W≤w.

[0011] Further, the outer diameter Φ of the first annular groove satisfies: d+4.5mm≤Φ≤D-2e; wherein d is the diameter of the central oil hole of the eccentric part, D is the outer diameter of the eccentric part, and e is the eccentric amount of the eccentric part;

[0012] The depth c of the second annular groove satisfies: 0<c≤0.25(n-m); wherein n is the outer circle diameter of the piston body, and m is the inner diameter of the piston body.

[0013] Further, the outer circle of the upper eccentric section is provided with a first radial oil hole and a first axial oil groove, the first radial oil hole is arranged near one side of the contact surface between the upper eccentric section and the upper hole wall section; wherein the starting end of the first radial oil hole is communicated with the central oil hole of the crankshaft body, and the terminal end of the first radial oil hole is communicated with the outer circle surface of the upper eccentric section;

[0014] The first axial oil groove is located between the contact surface of the upper eccentric section and the upper hole wall section, the starting end of the first axial oil groove is located at the center of the terminal end of the first radial oil hole, and the terminal end of the first axial oil groove is communicated with the upper end surface of the upper eccentric section.

[0015] Further, the outer circle of the lower eccentric section is provided with a second radial oil hole and a second axial oil groove;

[0016] The second radial oil hole is arranged close to one side of the contact surface between the lower eccentric section and the lower hole wall section; wherein the starting end of the second radial oil hole is communicated with the central oil hole of the crankshaft body, and the terminal end of the second radial oil hole is communicated with the outer circular surface of the lower eccentric section.

[0017] The second axial oil groove is located between the contact surface between the lower eccentric section and the lower hole wall section, the starting end of the second axial oil groove is located at the center of the terminal end of the second radial oil hole, and the terminal end of the second axial oil groove is communicated with the lower end surface of the lower eccentric section.

[0018] Further, the structural size of the first radial oil hole and the second radial oil hole is the same, and the oil hole diameter g of the first radial oil hole and the second radial oil hole satisfies: 0.05D≤g≤0.15D; wherein D is the outer diameter of the eccentric part.

[0019] Further, the structural size of the first axial oil groove and the second axial oil groove is the same, and the oil groove bottom width a of the first axial oil groove and the second axial oil groove satisfies: g≤a≤1.2g.

[0020] The application also provides a variable frequency rolling single rotor compressor comprising the crankshaft piston assembly.

[0021] The application also provides an air conditioner comprising the variable frequency rolling single rotor compressor.

[0022] Compared with the prior art, the application has the following beneficial effects:

[0023] The application provides a crankshaft piston assembly, a variable frequency rolling single rotor compressor and an air conditioner, by arranging a first annular groove on the outer circle of the eccentric part and a second annular groove on the inner hole wall of the piston body, the centrifugal inertia force and the inertia moment caused by the eccentric operation of the eccentric part and the piston are effectively reduced, so that the mass of the balance weight block of the motor rotor is effectively reduced, and the wind resistance is further reduced; at the same time, the contact surface between the eccentric part and the inner hole of the piston is reduced, the friction power consumption between the eccentric part and the piston is reduced, and the operating power of the compressor is effectively improved.

[0024] Further, the first annular groove is symmetrically distributed along the axial center section of the eccentric part, and the center line of the first annular groove is arranged to coincide with the rotation center axis of the crankshaft body, so that no centrifugal inertia force is generated in the eccentric part occupied by the groove during the operation of the compressor, and the mass of the balance weight block of the motor rotor is effectively reduced.

[0025] Further, according to the design principle that the axial extension length w of the first annular groove along the eccentric part satisfies: 0.1≤w / b≤0.6, the strength of the eccentric part is ensured to be reliable on the premise of reducing the mass of the eccentric part.

[0026] Further, by setting radial oil holes in the upper eccentric section and the lower eccentric section of the eccentric part, the lubricating oil in the central oil hole can pass through the radial oil holes to enter between the upper eccentric section and the upper hole wall section and between the lower eccentric section and the lower hole wall section, effectively improving the lubrication effect between the eccentric part and the piston, thereby reducing the friction loss between the crankshaft and the piston.

[0027] Further, by setting axial oil grooves in the upper eccentric section and the lower eccentric section of the eccentric part, on the one hand, the lubricating oil flowing out of the radial oil holes is guided to the space between the eccentric part and the piston; on the other hand, a sealing surface is formed between the outer circle of the eccentric part and the inner hole of the piston to the center position, preventing the refrigeration oil flowing out of the radial oil holes from flowing into the annular groove of the eccentric part and the piston. BRIEF DESCRIPTION OF DRAWINGS

[0028] Figure 1 It is a schematic diagram of the crankshaft body structure in Example 1;

[0029] Figure 2 It is an enlarged schematic diagram of the structure of the eccentric part in Example 1;

[0030] Figure 3 It is a dimension marking schematic diagram of the eccentric part in Example 1;

[0031] Figure 4 It is a schematic diagram of the piston body structure in Example 1;

[0032] Figure 5 It is a sectional view of the piston body in Example 1;

[0033] Figure 6 It is a schematic diagram of the structure of the variable frequency rolling single rotor compressor in Example 2.

[0034] Wherein, 11 is a crankshaft body, 12 is a piston body, 13 is a motor assembly, 14 is a cylinder; 111 is an eccentric part, 112 is a first annular groove, 113 is a central oil hole, 114 is a first radial oil hole, 115 is a first axial oil groove, 116 is a second radial oil hole, 117 is a second axial oil groove; 1111 is an upper eccentric section, 1112 is a lower eccentric section; 121 is a second annular groove, 122 is an upper hole wall section, 123 is a lower hole wall section. DETAILED DESCRIPTION

[0035] In order to make the technical problems solved by the present application, the technical solutions and beneficial effects more clear and explicit, the following specific embodiments are used to further illustrate the present application. It should be understood that the specific embodiments described herein are only used to explain the present application, and are not used to limit the present application.

[0036] The application provides a crankshaft piston assembly, which comprises a crankshaft body 11 and a piston body 12, the crankshaft body 11 is provided with an eccentric part 111, and the piston body 12 is sleeved on the outer circle of the eccentric part 111.

[0037] The outer circle of the eccentric part 111 is provided with a first annular groove 112, the first annular groove 112 divides the eccentric part 111 into an upper eccentric section 1111 and a lower eccentric section 1112, the first annular groove 112 is located in the middle of the eccentric part 111 and extends along the axial direction of the eccentric part 111, preferably, the first annular groove 112 is symmetrically distributed along the axial center section of the outer circle of the eccentric part 111, and the center line of the first annular groove 112 coincides with the rotation center axis of the crankshaft body 11.

[0038] The inner hole wall of the piston body 12 is provided with a second annular groove 121, the second annular groove 121 divides the inner hole wall of the piston body 12 into an upper hole wall section 122 and a lower hole wall section 123, the second annular groove 121 is located in the middle of the inner hole wall of the piston body 12 and extends along the axial direction of the piston body 12, the upper eccentric section 1111 cooperates with the upper hole wall section 122, and the lower eccentric section 1112 cooperates with the lower hole wall section 123.

[0039] In the application, the outer circle of the upper eccentric section 1111 is provided with a first radial oil hole 114 and a first axial oil groove 115, the first radial oil hole 114 is arranged close to the side of the contact surface between the upper eccentric section 1111 and the upper hole wall section 122, the starting end of the first radial oil hole 114 is communicated with the center oil hole 113 of the crankshaft body 11, and the terminal end of the first radial oil hole 114 is communicated with the outer circle surface of the upper eccentric section 1111, the first axial oil groove 115 is located between the contact surface between the upper eccentric section 1111 and the upper hole wall section 122, the starting end of the first axial oil groove 115 is located in the center of the terminal end of the first radial oil hole 114, and the terminal end of the first axial oil groove 115 is communicated with the upper end surface of the upper eccentric section 1111.

[0040] In the application, the outer circle of the lower eccentric section 1112 is provided with a second radial oil hole 116 and a second axial oil groove 117; the second radial oil hole 116 is arranged near one side of the contact surface between the lower eccentric section 1112 and the lower hole wall section 123; wherein the starting end of the second radial oil hole 116 is communicated with the central oil hole 113 of the crankshaft body 11, and the terminal end of the second radial oil hole 116 is communicated with the outer circle surface of the lower eccentric section 1112; the second axial oil groove 117 is located between the contact surface between the lower eccentric section 1112 and the lower hole wall section 123, and the starting end of the second axial oil groove 117 is located at the center of the terminal end of the second radial oil hole 116, and the terminal end of the second axial oil groove 117 is communicated with the lower end surface of the lower eccentric section 1112.

[0041] Working principle:

[0042] The crankshaft piston assembly provided by the application effectively reduces the centrifugal inertia force and inertia moment caused by the eccentric operation of the eccentric part and the piston, thereby effectively reducing the mass of the balance weight block of the motor rotor and further reducing the wind resistance; at the same time, the contact surface between the eccentric part and the inner hole of the piston is reduced, thereby reducing the friction power consumption between the eccentric part and the piston; the radial oil holes are arranged on the upper eccentric section and the lower eccentric section of the eccentric part, so that the lubricating oil in the central oil hole can enter between the upper eccentric section and the upper hole wall section and between the lower eccentric section and the lower hole wall section through the radial oil holes, thereby effectively improving the lubrication effect between the eccentric part and the piston and further reducing the friction loss between the crankshaft and the piston; the axial oil grooves are arranged on the upper eccentric section and the lower eccentric section of the eccentric part, which can guide the lubricating oil flowing out of the radial oil holes to the space between the eccentric part and the piston, and can form a sealing surface between the outer circle of the eccentric part and the inner hole of the piston towards the center position, thereby preventing the refrigeration machine oil flowing out of the radial oil holes from flowing into the annular grooves of the eccentric part and the piston.

[0043] The application further provides a variable frequency rolling single-rotor compressor comprising the crankshaft piston assembly.

[0044] The application further provides an air conditioner comprising the variable frequency rolling single-rotor compressor.

[0045] Embodiment 1

[0046] As shown in the accompanying drawings, Figures 1-5 Embodiment 1 provides a crankshaft piston assembly comprising a crankshaft body 11 and a piston body 12, the crankshaft body 11 comprising an axial long shaft part, an eccentric part 111 and a short shaft part connected in sequence; and the piston body 12 is sleeved on the outer circle of the eccentric part 111.

[0047] In the embodiment 1, the eccentric part 111 is provided with a first annular groove 112, which is symmetrically distributed along the axial center section O-O' of the eccentric part 111; the first annular groove 112 divides the eccentric part 111 into an upper eccentric section 1111 and a lower eccentric section 1112.

[0048] The axial extension length w of the first annular groove 112 along the eccentric part 111 satisfies: 0.1≤w / b≤0.6; wherein b is the total length of the eccentric part 111 in the axial direction; that is, the ratio of the axial width of the first annular groove 112 to the total length of the eccentric part 111 in the axial direction is 0.1-0.6; by using the first annular groove 112 to reduce the weight of the eccentric part 111, the strength of the eccentric part 111 is effectively ensured, and the reliability of the eccentric part 111 is ensured.

[0049] The first annular groove 112 is a cylindrical groove structure, and the center line of the first annular groove 112 coincides with the rotation center line of the crankshaft body 11; by setting the second annular groove 112, the eccentric part occupied by the first annular groove does not generate centrifugal inertia force during the operation of the compressor, effectively reducing the mass of the balance weight block of the motor rotor; preferably, the outer diameter Φ of the first annular groove 112 satisfies: d+4.5mm≤Φ≤D-2e; wherein d is the diameter of the central oil hole 113 of the eccentric part 111, D is the outer diameter of the eccentric part 111, and e is the eccentric amount of the eccentric part 111.

[0050] In the embodiment 1, the inner hole wall of the piston body 12 is provided with a second annular groove 121, and the second annular groove 121 divides the inner hole wall of the piston body 12 into an upper hole wall section 122 and a lower hole wall section 123; wherein the second annular groove 121 is located in the middle of the inner hole wall of the piston body 12 and extends in the axial direction of the piston body 12; the upper eccentric section 1111 cooperates with the upper hole wall section 122, and the lower eccentric section 1112 cooperates with the lower hole wall section 123.

[0051] The axial center section of the piston body 12 is set as section A-A', and the second annular groove 121 is symmetrically distributed on both sides of the center section A-A'; preferably, the axial extension length W of the second annular groove 121 along the piston body 12 satisfies: W≤w; that is, the axial width of the second annular groove 121 is less than or equal to the axial extension length w of the first annular groove along the eccentric part; the depth c of the second annular groove 121 satisfies: 0<c≤0.25(n-m); wherein n is the outer diameter of the piston body 12, and m is the inner diameter of the piston body 12.

[0052] In the embodiment 1, the center of the crankshaft body 11 is provided with a center oil hole 113 arranged along the axial direction of the crankshaft body 11; the outer circle of the upper eccentric section 1111 is provided with a first radial oil hole 114 and a first axial oil groove 115, the first radial oil hole 114 is arranged near the side of the contact surface between the upper eccentric section 1111 and the upper hole wall section 122; wherein the starting end of the first radial oil hole 114 is communicated with the center oil hole 113 of the crankshaft body 11, and the end of the first radial oil hole 114 is communicated with the outer circle surface of the upper eccentric section 1111; the first axial oil groove 115 is located between the contact surface between the upper eccentric section 1111 and the upper hole wall section 122, the starting end of the first axial oil groove 115 is located at the center of the end of the first radial oil hole 114, and the end of the first axial oil groove 115 is communicated with the upper end surface of the upper eccentric section 1111.

[0053] The outer circle of the lower eccentric section 1112 is provided with a second radial oil hole 116 and a second axial oil groove 117; the second radial oil hole 116 is arranged near the side of the contact surface between the lower eccentric section 1112 and the lower hole wall section 123; wherein the starting end of the second radial oil hole 116 is communicated with the center oil hole 113 of the crankshaft body 11, and the end of the second radial oil hole 116 is communicated with the outer circle surface of the lower eccentric section 1112; the second axial oil groove 117 is located between the contact surface between the lower eccentric section 1112 and the lower hole wall section 123, the starting end of the second axial oil groove 117 is located at the center of the end of the second radial oil hole 116, and the end of the second axial oil groove 117 is communicated with the lower end surface of the lower eccentric section 1112.

[0054] The structure size of the first radial oil hole 114 and the second radial oil hole 116 is the same, the oil hole diameter g of the first radial oil hole 114 and the second radial oil hole 116 satisfies: 0.05D≤g≤0.15D; wherein D is the outer diameter of the eccentric part 111; the structure size of the first axial oil groove 115 and the second axial oil groove 117 is the same, the oil groove bottom width a of the first axial oil groove 115 and the second axial oil groove 117 satisfies: g≤a≤1.2g.

[0055] In the embodiment 1, the radial oil hole is arranged on the upper eccentric section and the lower eccentric section, the starting end of the radial oil hole is communicated with the central oil hole of the center of the crankshaft body, and the end of the radial oil hole penetrates the outer circular surface of the upper eccentric section or the lower eccentric section. Thus, the lubricating oil in the central oil hole can enter the contact surface between the upper eccentric section or the lower eccentric section and the piston body through the radial oil hole, so as to improve the lubrication between the eccentric part and the piston body and reduce the friction loss. The axial oil groove is arranged on the upper eccentric section and the lower eccentric section, the starting end of the axial oil groove is communicated with the center of the end of the radial oil hole, that is, the starting position of the axial oil groove is the center of the axial oil hole, and the axial oil groove extends to the upper and lower end surfaces of the eccentric part. On the one hand, the refrigerant oil flowing out of the radial oil hole can be guided to the contact surface between the upper eccentric section and the upper hole wall section or the contact surface between the lower eccentric section and the lower hole wall section. At the same time, a predetermined length of sealing surface can be formed between the eccentric part and the inner wall of the piston body, so as to prevent the refrigerant oil flowing out of the radial oil hole from flowing into the first annular groove of the eccentric part and the second annular groove of the piston body.

[0056] The crankshaft piston assembly in the embodiment 1 can reduce the weight of the eccentric part by more than 30% by arranging the first annular groove on the outer circle of the eccentric part. When the compressor rotates, the piston body rotates with the eccentric part at a circumference with an eccentric amount e. The centrifugal inertia force generated by the piston body is about 1.5 times or more than that of the eccentric part. Therefore, it is particularly important to reduce the mass of the piston. Therefore, the second annular groove is arranged on the inner hole wall of the piston body to reduce the centrifugal inertia force of the piston body. At the same time, the contact surface between the piston body and the eccentric part is effectively reduced, and the friction power consumption is reduced.

[0057] Embodiment 2

[0058] As shown in the accompanying drawings, Figure 6 The embodiment 2 provides a variable frequency rolling single rotor compressor, which comprises a shell, a motor assembly 13, a pump body assembly and a liquid accumulator assembly. The motor assembly and the pump body assembly are arranged in the shell, and the motor assembly is arranged above the pump body assembly. The pump body assembly comprises a cylinder 14, a crankshaft and a piston. The crankshaft adopts the crankshaft body 11 in the crankshaft piston assembly in the embodiment 1, and the piston adopts the piston body 12 in the crankshaft piston assembly in the embodiment 1. The long axis part of the crankshaft body 11 is connected with the motor assembly, the eccentric part 111 of the crankshaft body 11 is arranged in the working cavity of the cylinder, and the piston body 12 is sleeved on the eccentric part 111.

[0059] It should be noted that, in the variable frequency rolling single rotor compressor, the crankshaft and the piston adopt the crankshaft piston assembly as described in the embodiment, and the remaining structures are the same as those of the conventional compressor, which will not be described here.

[0060] In the embodiments 1 and 2, the first annular groove 112 is arranged on the outer circle of the eccentric part 111 of the crankshaft body 11, and the second annular groove 121 is arranged on the inner hole wall of the piston body 12, so that the centrifugal inertia force and the inertia moment caused by the eccentric operation of the eccentric part and the piston of the rolling single rotor compressor can be greatly reduced, the balance weight mass of the motor rotor can be effectively reduced, the wind resistance can be reduced, the contact area between the eccentric part and the piston can be reduced, the friction power consumption between the eccentric part and the piston can be reduced, and the operation power of the compressor can be further improved.

[0061] The embodiment 2 further provides an air conditioner, which comprises the variable frequency rolling single rotor compressor described above, so that the pipeline vibration of the air conditioner can be effectively improved, and the operation power of the air conditioner can be reduced; preferably, the air conditioner is an air conditioner with a capacity of 2 or more; and the variable frequency rolling single rotor compressor is a compressor with a capacity of 2 or more.

[0062] The crankshaft piston assembly, the rolling single rotor variable frequency compressor and the air conditioner provided by the application, wherein the power transmission of the compressor is mainly completed by the crankshaft body 11; the eccentric part 111 is arranged on the crankshaft body 11, the central axis of the eccentric part 111 is arranged eccentrically relative to the rotation center of the crankshaft body 11, the eccentric part 111 is provided with radial oil holes and axial oil grooves, and the piston body 12 is sleeved on the outer circle of the eccentric part; the long shaft part of the crankshaft is sleeved in the motor rotor; during the operation of the compressor, the crankshaft body 11 drives the piston body 12 to rotate away from the rotation center of the crankshaft body under the driving of the motor stator and the motor rotor; at present, the cylinder volume required by a compressor with a capacity of 2 or more is large, and the cylinder height or the eccentric distance of the crankshaft is usually increased to achieve this requirement, and both of the above methods increase the centrifugal inertia force and the inertia moment of the rolling single rotor compressor during operation; in the application, the first annular groove is arranged on the outer circle of the eccentric part, and the second annular groove is arranged on the inner hole wall of the piston body, so that the centrifugal inertia force and the inertia moment caused by the eccentric operation of the eccentric part and the piston can be effectively reduced, the balance weight mass of the motor rotor can be effectively reduced, the wind resistance can be reduced, the contact area between the eccentric part and the piston can be reduced, the friction power consumption between the eccentric part and the piston can be reduced, and the operation power of the compressor can be effectively improved.

[0063] The above embodiments are only one of the implementation manners of the technical scheme of the application, and the scope of the application claimed by the application is not limited to the above embodiments, but also includes any changes, substitutions and other implementation manners easily thought of by those skilled in the art within the technical scope disclosed by the application.

Claims

1. A crankshaft piston assembly, characterized in that, It includes a crankshaft body (11) and a piston body (12); the crankshaft body (11) is provided with an eccentric part (111), and the piston body (12) is sleeved on the outer circle of the eccentric part (111); The outer circumference of the eccentric portion (111) is provided with a first annular groove (112), which divides the eccentric portion (111) into an upper eccentric segment (1111) and a lower eccentric segment (1112); wherein, the first annular groove (112) is located in the middle of the eccentric portion (111) and extends along the axial direction of the eccentric portion (111); The piston body (12) has a second annular groove (121) on its inner wall, which divides the inner wall of the piston body (12) into an upper wall section (122) and a lower wall section (123). The second annular groove (121) is located in the middle of the inner wall of the piston body (12) and extends along the axial direction of the piston body (12). The upper eccentric section (1111) cooperates with the upper wall section (122), and the lower eccentric section (1112) cooperates with the lower wall section (123). The first annular groove (112) is symmetrically distributed along the central section of the outer circle of the eccentric part (111), and the center line of the first annular groove (112) coincides with the rotation center axis of the crankshaft body (11). The first annular groove (112) extends along the axial length w of the eccentric portion (111) to satisfy: 0.1≤w / b≤0.6; where b is the total axial length of the eccentric portion (111); the outer diameter Φ of the first annular groove (112) satisfies: d+4.5mm≤Φ≤D-2e; where d is the diameter of the central oil hole (113) of the eccentric portion (111), D is the outer diameter of the eccentric portion (111), and e is the eccentricity of the eccentric portion (111); A first radial oil hole (114) and a first axial oil groove (115) are provided on the outer circle of the upper eccentric section (1111). The first radial oil hole (114) is provided on the side close to the contact surface between the upper eccentric section (1111) and the upper hole wall section (122). The starting end of the first radial oil hole (114) is connected to the central oil hole (113) of the crankshaft body (11), and the end of the first radial oil hole (114) is connected to the outer circle surface of the upper eccentric section (1111). The first axial oil groove (115) is located between the contact surfaces of the upper eccentric section (1111) and the upper hole wall section (122). The starting end of the first axial oil groove (115) is located at the end center of the first radial oil hole (114). The end of the first axial oil groove (115) is connected to the upper end face of the upper eccentric section (1111). The outer circle of the lower eccentric section (1112) is provided with a second radial oil hole (116) and a second axial oil groove (117). The second radial oil hole (116) is arranged close to one side of the contact surface between the lower eccentric section (1112) and the lower hole wall section (123); wherein, the starting end of the second radial oil hole (116) is communicated with the central oil hole (113) of the crankshaft body (11), and the ending end of the second radial oil hole (116) is communicated with the outer circular surface of the lower eccentric section (1112). The second axial oil groove (117) is located between the contact surface of the lower eccentric section (1112) and the lower hole wall section (123), the starting end of the second axial oil groove (117) is located at the center of the ending end of the second radial oil hole (116), and the ending end of the second axial oil groove (117) is communicated with the lower end surface of the lower eccentric section (1112).

2. A crankshaft piston assembly according to claim 1, characterized in that, The axial extension length W of the second annular groove (121) along the piston body (12) satisfies: W ≤ w; the depth c of the second annular groove (121) satisfies: 0 < c ≤ 0.25(n - m); wherein, n is the outer diameter of the piston body (12), and m is the inner diameter of the piston body (12).

3. A crankshaft piston assembly according to claim 1, characterized in that, The first radial oil hole (114) and the second radial oil hole (116) have the same structural dimensions, and the oil hole diameters g of the first radial oil hole (114) and the second radial oil hole (116) both satisfy: 0.05D ≤ g ≤ 0.15D; wherein, D is the outer diameter of the eccentric part (111).

4. A crankshaft piston assembly according to claim 1, characterized in that, The first axial oil groove (115) and the second axial oil groove (117) have the same structural dimensions, and the bottom width a of the oil grooves of the first axial oil groove (115) and the second axial oil groove (117) satisfies: g ≤ a ≤ 1.2g.

5. A variable frequency rolling single-rotor compressor, characterized in that, It includes a crankshaft piston assembly according to any one of claims 1 - 4.

6. An air conditioner, characterized in that, It includes a variable frequency rolling single rotor compressor according to claim 5.

Images