CN219795567U - Crankshaft piston assembly, variable-frequency rolling single-rotor compressor and air conditioner - Google Patents

Abstract

The utility model discloses a crankshaft piston assembly, a variable-frequency rolling single-rotor compressor and an air conditioner, comprising a crankshaft body and a piston body; the crankshaft body is provided with an eccentric part, and the piston body is sleeved on the outer circle of the eccentric part; the outer circle of the eccentric part is provided with a first annular groove, and the eccentric part is divided into an upper eccentric section and a lower eccentric section; the first annular groove is positioned in the middle of the eccentric part; the inner hole wall of the piston body is provided with a second annular groove, 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 positioned 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 utility model effectively reduces the centrifugal inertia force and the inertia moment of the eccentric part and the piston, thereby effectively reducing the mass of the balancing weight of the motor rotor and further reducing the wind 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

Crankshaft piston assembly, variable-frequency rolling single-rotor compressor and air conditioner

Technical Field

The utility model belongs to the technical field of compressors, and particularly relates to a crankshaft piston assembly, a variable-frequency rolling single-rotor compressor and an air conditioner.

Background

Currently, 2 or more compressors for variable frequency air conditioners commonly adopt a double-rotor structure; wherein, two eccentric parts of the crankshaft are oppositely arranged at 180 degrees, and two rolling pistons arranged on the eccentric parts work simultaneously at a rotation angle difference of 180 degrees; the symmetrical structure in the double-rotor compressor balances the self-rotation inertia force, and only needs to balance the rotation inertia moment generated by the two eccentric masses on the same plane; the balancing weight of the motor is small in mass and low in height, and running wind resistance generated by the balancing weight is small and the vibration of the whole machine is low.

With the development of compressor technology, 2 or more compressors are gradually converted from a double-rotor structure to a single-rotor structure; compared with 1 compressor, the heights of the cylinders and the pistons of 2 single-rotor compressors and more are increased, so that the contact area between the eccentric part of the crankshaft and the inner hole of the piston is increased, and the friction power consumption between the eccentric part of the crankshaft and the inner hole of the piston is increased; for example, when the cylinder inner diameter is 43mm and the crank eccentricity is not changed, the height of the cylinder and the piston is increased by 31%; meanwhile, in the single rotor compressor, the structure is the eccentric rotation characteristic of the eccentric part and the piston; therefore, centrifugal inertia force generated during the operation of the compressor cannot be balanced and needs to be counteracted by balancing weights at two ends of a motor rotor; but on one hand, the unbalanced force of the balancing weight is increased due to the increase of the heights of the eccentric part and the piston, and on the other hand, the centrifugal inertial force of the eccentric part and the piston is needed to be counteracted due to the fact that a symmetrical structure is not provided, so that the balancing weight has large mass and much higher than that of the double rotors, and then the wind resistance of the balancing weight is increased when the compressor operates, and the vibration and the power of the whole machine are deteriorated.

Disclosure of Invention

Aiming at the technical problems in the prior art, the utility model provides a crankshaft piston assembly, a variable-frequency rolling single-rotor compressor and an air conditioner, which are used for solving the problems that the heights of cylinders and pistons of the existing 2 or more single-rotor compressors are increased, so that the contact area between an eccentric part of a crankshaft and an inner hole of a piston is increased, and the friction power consumption between the eccentric part and the inner hole of the piston is increased; meanwhile, when the compressor operates, the windage of the balancing weight is increased, so that the technical problems of vibration and power deterioration of the whole machine are caused.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

the utility model provides a crankshaft piston assembly, which comprises a crankshaft body and a piston body; the crankshaft body is provided with an eccentric part, and the piston body is sleeved on the outer circle of the eccentric part;

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; the first annular groove is positioned in the middle of the eccentric part and extends along the axial direction of the eccentric part;

a second annular groove is formed in the inner hole wall of the piston body, and divides the inner hole wall of the piston body into an upper hole wall section and a lower hole wall section; the second annular groove is positioned 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 is matched with the upper hole wall section, and the lower eccentric section is matched with the lower hole wall section.

Further, the first annular grooves are symmetrically distributed along the outer circle axial center section of the eccentric part, and the center line of the first annular grooves coincides with the rotation center axis of the crankshaft body.

Further, the axial extension w of the first annular groove along the eccentric portion satisfies: w/b is more than or equal to 0.1 and less than or equal to 0.6; wherein b is the total axial length of the eccentric part; the second annular groove satisfies the following along the axial extension length W of the piston body: w is less than or equal to W.

Further, the outer diameter Φ of the first annular groove satisfies: d+4.5mm.ltoreq.phi.ltoreq.D-2 e; 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;

the depth c of the second annular groove satisfies: 0<c is less than or equal to 0.25 (n-m); wherein n is the diameter of the outer circle of the piston body, and m is the inner diameter of the piston body.

Further, a first radial oil hole and a first axial oil groove are formed in the outer circle of the upper eccentric section, and the first radial oil hole is arranged close to one side of the contact surface of the upper eccentric section and the upper hole wall section; the starting end of the first radial oil hole is communicated with the central oil hole of the crankshaft body, and the tail end of the first radial oil hole is communicated with the outer circle surface of the upper eccentric section;

the first axial oil groove is positioned between the contact surface of the upper eccentric section and the upper hole wall section, the initial end of the first axial oil groove is positioned at the center of the tail end of the first radial oil hole, and the tail end of the first axial oil groove is communicated with the upper end surface of the upper eccentric section.

Further, a second radial oil hole and a second axial oil groove are formed in the outer circle of the lower eccentric section;

the second radial oil hole is arranged close to one side of the contact surface of the lower eccentric section and the lower hole wall section; the starting end of the second radial oil hole is communicated with the central oil hole of the crankshaft body, and the tail end of the second radial oil hole is communicated with the outer circle surface of the lower eccentric section;

the second axial oil groove is positioned between the contact surfaces of the lower eccentric section and the lower hole wall section, the initial end of the second axial oil groove is positioned at the center of the tail end of the second radial oil hole, and the tail end of the second axial oil groove is communicated with the lower end surface of the lower eccentric section.

Further, the first radial oil hole and the second radial oil hole have the same structural size, and the oil hole diameters g of the first radial oil hole and the second radial oil hole all satisfy: g is more than or equal to 0.05D and less than or equal to 0.15D; wherein D is the outer diameter of the eccentric portion.

Further, the first axial oil groove and the second axial oil groove have the same structural dimensions, and the oil groove bottom widths a of the first axial oil groove and the second axial oil groove satisfy: g is more than or equal to a and less than or equal to 1.2g.

The utility model also provides a variable-frequency rolling single-rotor compressor, which comprises the crankshaft piston assembly.

The utility model also provides an air conditioner comprising the variable-frequency rolling single-rotor compressor.

Compared with the prior art, the utility model has the beneficial effects that:

the utility model provides a crankshaft piston assembly, a variable-frequency rolling single-rotor compressor and an air conditioner, wherein a first annular groove is formed in the outer circle of an eccentric part, and a second annular groove is formed in the inner hole wall of a piston body, so that centrifugal inertia force and inertia moment caused by eccentric operation of the eccentric part and a piston are effectively reduced, the balancing weight mass of a motor rotor is effectively reduced, and wind resistance is further reduced; meanwhile, the contact surface between the eccentric part and the inner hole of the piston is reduced, so that the friction power consumption between the eccentric part and the piston is reduced, and the operation power of the compressor is further effectively improved.

Further, the first annular grooves are symmetrically distributed along the outer circle axial center section of the eccentric part, the center line of the first annular grooves is overlapped with the rotation center axis of the crankshaft body, so that eccentric parts occupied by the grooves in the operation process of the compressor are free from centrifugal inertia force, and the mass of the balancing weight of the motor rotor is effectively reduced.

Further, according to the axial extension w of the first annular groove along the eccentric portion, the following is satisfied: the design principle that w/b is more than or equal to 0.1 and less than or equal to 0.6 is realized, and the strength of the eccentric part is ensured to be reliable on the premise of weight reduction of the eccentric part.

Further, through all setting up radial oilhole at the upper eccentric section and the lower eccentric section of eccentric part to make the lubricating oil of central oilhole can enter into between upper eccentric section and the upper pore wall section and between lower eccentric section and the lower pore wall section through radial oilhole, effectively improved the lubrication effect between eccentric part and the piston, and then reduced the friction loss between bent axle and the piston.

Further, by arranging the axial oil grooves on the upper eccentric section and the lower eccentric section of the eccentric part, on one hand, the lubricating oil flowing out of the radial oil hole is guided between the eccentric part and the piston; on the other hand, the outer circle of the eccentric part and the inner hole of the piston form a sealing surface towards the center, so that the refrigerating machine oil flowing out of the radial oil hole is prevented from flowing into the annular grooves of the eccentric part and the piston.

Drawings

Fig. 1 is a schematic view of a crankshaft body structure in embodiment 1;

fig. 2 is an enlarged schematic view of the structure of the eccentric portion in embodiment 1;

FIG. 3 is a schematic illustration of the dimensioning of the eccentric portion in example 1;

fig. 4 is a schematic perspective view of the piston body in embodiment 1;

fig. 5 is a sectional view of the piston body in embodiment 1;

fig. 6 is a schematic structural diagram of a variable frequency rolling single rotor compressor according to embodiment 2.

The device comprises a crankshaft body 11, a piston body 12, a motor assembly 13 and a cylinder 14; 111 eccentric portion, 112 first annular groove, 113 central oil hole, 114 first radial oil hole, 115 first axial oil groove, 116 second radial oil hole, 117 second axial oil groove; 1111 upper eccentric section, 1112 lower eccentric section; 121, a second annular groove, 122 an upper bore wall section, 123 a lower bore wall section.

Detailed Description

In order to make the technical problems, technical schemes and beneficial effects solved by the utility model more clear, the following specific embodiments are used for further describing the utility model in detail. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the utility model.

The utility model provides a crankshaft piston assembly, which comprises a crankshaft body 11 and a piston body 12, wherein an eccentric part 111 is arranged on the crankshaft body 11, and the piston body 12 is sleeved on the outer circle of the eccentric part 111.

A first annular groove 112 is arranged on the outer circle of the eccentric part 111, and the first annular groove 112 divides the eccentric part 111 into an upper eccentric section 1111 and a lower eccentric section 1112; wherein the first annular groove 112 is located at the middle of the eccentric portion 111 and extends along the axial direction of the eccentric portion 111; preferably, the first annular grooves 112 are symmetrically distributed along an outer circumferential axial center section of the eccentric portion 111, and a center line of the first annular grooves 112 coincides with a rotation center axis of the crankshaft body 11.

A second annular groove 121 is arranged on the inner hole wall of the piston body 12, 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 at 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 mates with the upper bore wall section 122 and the lower eccentric section 1112 mates with the lower bore wall section 123.

In the present utility model, 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, and the first radial oil hole 114 is provided near one 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 central oil hole 113 of the crankshaft body 11, and the tail end of the first radial oil hole 114 is communicated with the outer circular 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 start 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.

In the utility model, 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 of the lower eccentric section 1112 and the lower hole wall section 123; wherein, the initial end of the second radial oil hole 116 is communicated with the central oil hole 113 of the crankshaft body 11, and the tail 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 start 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.

Working principle:

according to the crankshaft piston assembly, the first annular groove is formed in the outer circle of the eccentric part, and the second annular groove is formed in the inner hole wall of the piston body, so that centrifugal inertial force and inertial moment caused by eccentric operation of the eccentric part and the piston are effectively reduced, the balancing weight mass of the motor rotor is effectively reduced, and wind resistance is further reduced; meanwhile, the contact surface between the eccentric part and the inner hole of the piston is reduced, so that the friction power consumption between the eccentric part and the piston is reduced; the radial oil holes are formed in the upper eccentric section and the lower eccentric section of the eccentric part, so that 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, the lubricating effect between the eccentric part and the piston is effectively improved, and further the friction loss between the crankshaft and the piston is reduced; by arranging the axial oil grooves on the upper eccentric section and the lower eccentric section of the eccentric part, on one hand, the lubricating oil flowing out of the radial oil hole is guided between the eccentric part and the piston; on the other hand, the outer circle of the eccentric part and the inner hole of the piston form a sealing surface towards the center, so that the refrigerating machine oil flowing out of the radial oil hole is prevented from flowing into the annular grooves of the eccentric part and the piston.

The utility model also provides a variable-frequency rolling single-rotor compressor, which comprises the crankshaft piston assembly.

The utility model also provides an air conditioner comprising the variable-frequency rolling single-rotor compressor.

Example 1

As shown in fig. 1 to 5, embodiment 1 provides a crankshaft piston assembly, which includes a crankshaft body 11 and a piston body 12, wherein the crankshaft body 11 includes a long shaft portion, an eccentric portion 111 and a short shaft portion which are axially connected in sequence; the piston body 12 is sleeved on the outer circle of the eccentric portion 111.

In this embodiment 1, a first annular groove 112 is disposed on the outer circumference of the eccentric portion 111, and the first annular groove 112 is symmetrically distributed along the axial center section O-O' of the outer circumference of the eccentric portion 111; the first annular groove 112 divides the eccentric portion 111 into an upper eccentric section 1111 and a lower eccentric section 1112.

The first annular groove 112 satisfies the following along the axial extension w of the eccentric portion 111: w/b is more than or equal to 0.1 and less than or equal to 0.6; wherein b is the total axial length of the eccentric portion 111; i.e., the ratio of the axial width of the first annular groove 112 to the total axial length of the eccentric portion 111 is 0.1-0.6; the first annular groove 112 is used for reducing the weight of the eccentric portion 111, meanwhile, the strength of the eccentric portion 111 is effectively ensured, and the reliability of the eccentric portion 111 is ensured.

The first annular groove 112 has 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 arranging the second annular groove 112, the eccentric part occupied by the first annular groove is free from centrifugal inertia force in the running process of the compressor, and the balancing weight mass of the motor rotor is effectively reduced; preferably, the outer diameter Φ of the first annular groove 112 satisfies: d+4.5mm.ltoreq.phi.ltoreq.D-2 e; where D is the diameter of the center oil hole 113 of the eccentric portion 111, D is the outer diameter of the eccentric portion 111, and e is the eccentric amount of the eccentric portion 111.

In this embodiment 1, a second annular groove 121 is disposed on the inner hole wall of the piston body 12, 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 at 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 mates with the upper bore wall section 122 and the lower eccentric section 1112 mates with the lower bore wall section 123.

Setting the axial central section of the piston body 12 as a section A-A ', wherein the second annular grooves 121 are symmetrically distributed on two sides of the central section A-A'; preferably, the second annular groove 121 extends along the axial direction of the piston body 12 by a length W, which satisfies the following conditions: w is less than or equal to W; that is, the axial width of the second annular groove 121 is equal to or less than the axial extension w of the first annular groove along the eccentric portion; the depth c of the second annular groove 121 satisfies: 0<c is less than or equal to 0.25 (n-m); where n is the outer diameter of the piston body 12 and m is the inner diameter of the piston body 12.

In the present embodiment 1, a center oil hole 113 is provided in the center of the crankshaft body 11, and the center oil hole 113 is provided along the axial direction of the crankshaft body 11; a first radial oil hole 114 and a first axial oil groove 115 are arranged on the outer circle of the upper eccentric section 1111, and the first radial oil hole 114 is arranged near one 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 central oil hole 113 of the crankshaft body 11, and the tail end of the first radial oil hole 114 is communicated with the outer circular 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 start 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.

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 of the lower eccentric section 1112 and the lower hole wall section 123; wherein, the initial end of the second radial oil hole 116 is communicated with the central oil hole 113 of the crankshaft body 11, and the tail 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 start 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.

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 satisfy: g is more than or equal to 0.05D and less than or equal to 0.15D; wherein D is the outer diameter of the eccentric portion 111; the first axial oil groove 115 and the second axial oil groove 117 have the same structural dimensions, and the oil groove bottom widths a of the first axial oil groove 115 and the second axial oil groove 117 satisfy: g is more than or equal to a and less than or equal to 1.2g.

In the embodiment 1, radial oil holes are formed in both the upper eccentric section and the lower eccentric section, the starting end of each radial oil hole is communicated with the central oil hole in the center of the crankshaft body, and the tail end of each radial oil hole penetrates through the outer circular surface of the upper eccentric section or the lower eccentric section; therefore, 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 that the lubrication between the eccentric part and the piston body is improved, and the friction loss is reduced; through arranging the axial oil grooves on the upper eccentric section and the lower eccentric section, the initial end of the axial oil groove is communicated with the tail end center of the radial oil hole, namely, the initial position of the axial oil groove point is the center of the axial oil hole and extends and penetrates through the upper end face and the lower end face of the eccentric section, on one hand, refrigerating machine oil flowing out of the radial oil hole can be guided to a contact surface between the upper eccentric section and the upper hole wall section or a contact surface between the lower eccentric section and the lower hole wall section; meanwhile, a sealing surface with a preset length can be formed between the eccentric part and the inner wall of the piston body, so that refrigerating machine oil flowing out of the radial oil hole is prevented from flowing into the first annular groove of the eccentric part and the second annular groove of the piston body.

In the crankshaft piston assembly according to embodiment 1, the weight of the eccentric portion can be reduced by more than 30% by providing the first annular groove on the outer circumference of the eccentric portion; because the piston body is sleeved on the outer circle of the eccentric part, when the compressor rotates, the piston body rotates along with the eccentric part by the circumference with the eccentric value of e, and the centrifugal inertia force generated by the piston body is more than 1.5 times of that of the eccentric part; therefore, reducing the mass of the piston is particularly important; therefore, the purpose of reducing the centrifugal inertia force of the piston body is achieved by arranging the second annular groove on the inner hole wall of the piston body; meanwhile, the contact surface between the piston body and the eccentric part is effectively reduced, and further friction power consumption is reduced.

Example 2

As shown in fig. 6, embodiment 2 provides a variable frequency rolling single rotor compressor, which comprises a housing, a motor assembly 13, a pump body assembly and a liquid reservoir assembly; the motor assembly and the pump body assembly are arranged inside 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, wherein the crankshaft adopts a crankshaft body 11 in the crankshaft piston assembly in the embodiment 1, and the piston adopts a piston body 12 in the crankshaft piston assembly in the embodiment 1; the long shaft 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.

It should be noted that, in the variable-frequency rolling single-rotor compressor, except for the crankshaft and the piston, the crankshaft piston assembly described in the embodiment is adopted, and the other structures are the same as those of the conventional compressor, and are not described herein again.

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

The embodiment 2 also provides an air conditioner, which comprises the variable-frequency rolling single-rotor compressor, so that the pipeline vibration of the air conditioner can be effectively improved, and the running power of the air conditioner can be reduced; preferably, the air conditioner is 2 or more air conditioners; the variable-frequency rolling single-rotor compressor is 2 or more compressors.

The utility model relates to a crankshaft piston assembly, a rolling single-rotor variable frequency compressor and an air conditioner, wherein the power transmission of the compressor is mainly completed by a crankshaft body 11; by arranging the eccentric part 111 on the crankshaft body 11, the central axis of the eccentric part 111 is eccentrically arranged relative to the rotation center of the crankshaft body 11, the eccentric part 111 is provided with a radial oil hole and an axial oil groove, and the piston body 12 is sleeved on the outer circle of the eccentric part; the long shaft part of the crankshaft is thermally sleeved in the motor rotor; when the compressor runs, the crankshaft body 11 is driven by the motor stator and the motor rotor to drive the piston body 12 to deviate from the rotation center of the crankshaft body for rotation; at present, due to the large cylinder volume required by 2 and more compressors, the high cylinder and piston heights or the eccentric distance of a crankshaft are usually increased, and the centrifugal inertia force and the inertia moment of the running single-rotor compressor are increased by the two methods; in the utility model, 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 are effectively reduced, the balancing weight mass of the motor rotor is effectively reduced, and the wind resistance is further reduced; meanwhile, the contact surface between the eccentric part and the inner hole of the piston is reduced, so that the friction power consumption between the eccentric part and the piston is reduced, and the operation power of the compressor is further effectively improved.

The above embodiment is only one of the implementation manners capable of implementing the technical solution of the present utility model, and the scope of the claimed utility model is not limited to the embodiment, but also includes any changes, substitutions and other implementation manners easily recognized by those skilled in the art within the technical scope of the present utility model.

Claims (10)

1. A crankshaft piston assembly, characterized by comprising a crankshaft body (11) and a piston body (12); an eccentric part (111) is arranged on the crankshaft body (11), and the piston body (12) is sleeved on the outer circle of the eccentric part (111);

a first annular groove (112) is formed in the outer circle of the eccentric part (111), and the first annular groove (112) divides the eccentric part (111) into an upper eccentric section (1111) and a lower eccentric section (1112); wherein the first annular groove (112) is positioned in the middle of the eccentric part (111) and extends along the axial direction of the eccentric part (111);

a second annular groove (121) is formed in the inner hole wall of the piston body (12), 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 positioned 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 bore wall section (122), and the lower eccentric section (1112) cooperates with the lower bore wall section (123).

2. A crankshaft piston assembly according to claim 1, wherein the first annular grooves (112) are symmetrically distributed along an outer circumferential axial center section of the eccentric portion (111), and a center line of the first annular grooves (112) coincides with a rotation center axis of the crankshaft body (11).

3. A crankshaft piston assembly according to claim 1, wherein the first annular groove (112) has an axial extension w along the eccentric portion (111) that satisfies: w/b is more than or equal to 0.1 and less than or equal to 0.6; wherein b is the total axial length of the eccentric part (111); the outer diameter Φ of the first annular groove (112) satisfies: d+4.5mm.ltoreq.phi.ltoreq.D-2 e; 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).

4. A crankshaft piston assembly according to claim 1, wherein the second annular groove (121) satisfies along the axial extension W of the piston body (12): w is less than or equal to W; the depth c of the second annular groove (121) satisfies: 0<c is less than or equal to 0.25 (n-m); wherein n is the diameter of the outer circle of the piston body (12), and m is the inner diameter of the piston body (12).

5. A crankshaft piston assembly according to claim 1, wherein a first radial oil hole (114) and a first axial oil groove (115) are formed in the outer circle of the upper eccentric section (1111), and the first radial oil hole (114) is arranged near the contact surface side of 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 a central oil hole (113) of the crankshaft body (11), and the tail end of the first radial oil hole (114) is communicated with the outer circular surface of the upper eccentric section (1111);

the first axial oil groove (115) is located between the contact surface of the upper eccentric section (1111) and the upper hole wall section (122), the initial end of the first axial oil groove (115) is located at the center of the tail end of the first radial oil hole (114), and the tail end of the first axial oil groove (115) is communicated with the upper end surface of the upper eccentric section (1111).

6. A crankshaft piston assembly according to claim 5, wherein the outer circumference 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 of the lower eccentric section (1112) and the lower hole wall section (123); the starting end of the second radial oil hole (116) is communicated with a central oil hole (113) of the crankshaft body (11), and the tail 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 initial end of the second axial oil groove (117) is located at the tail end center of the second radial oil hole (116), and the tail end of the second axial oil groove (117) is communicated with the lower end surface of the lower eccentric section (1112).

7. The crankshaft piston assembly according to claim 6, wherein 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) are all satisfied: g is more than or equal to 0.05D and less than or equal to 0.15D; wherein D is the outer diameter of the eccentric part (111).

8. A crankshaft piston assembly according to claim 6, wherein the first axial oil groove (115) and the second axial oil groove (117) are identical in structural size, and the oil groove bottom widths a of the first axial oil groove (115) and the second axial oil groove (117) satisfy: g is more than or equal to a and less than or equal to 1.2g.

9. A variable frequency rolling single rotor compressor comprising a crankshaft piston assembly as claimed in any one of claims 1 to 8.

10. An air conditioner comprising a variable frequency rolling single rotor compressor as claimed in claim 9.