CN215927782U - Pump body assembly, rotary compressor and refrigeration equipment - Google Patents

Abstract

The utility model discloses a pump body assembly, a rotary compressor and refrigeration equipment. The pump body assembly includes a crankshaft, a first bearing, a second bearing, and a roller. The crankshaft comprises a first shaft part, an eccentric part and a second shaft part which are sequentially connected, a first bearing is connected to the first shaft part, and a second bearing is connected to the second shaft part; the roller is arranged on the eccentric part, two end surfaces of the roller are respectively connected with the inner surfaces of the first bearing and the second bearing in a sliding fit mode, and the inner circumferential surface of the roller is connected with the outer circumferential surface of the eccentric part in a sliding fit mode. One side where one of the first bearing and the second bearing is located is an exhaust side of the pump body assembly, and a notch portion is arranged on the end face, far away from the exhaust side, of the roller. The end surface of the roller is provided with the notch part, so that the friction power loss between the roller and the roller can be reduced to a certain degree, and the efficiency of the compressor can be effectively improved.

Description

Pump body assembly, rotary compressor and refrigeration equipment

Technical Field

The utility model relates to the technical field of compressors, in particular to a pump body assembly, a rotary compressor and refrigeration equipment.

Background

In the related art, a pump body assembly of a rotary compressor includes a cylinder, a crankshaft, a roller, an upper bearing, a lower bearing, a vane, and the like. The roller is connected to an eccentric portion of the crankshaft, and compresses gas by changing a volume in a cylinder by rotation of the roller in the cylinder. It will be appreciated that these components are subject to friction during various relative movements, such as sliding friction between the roller and the eccentric portion of the crankshaft, rolling friction between the roller and the cylinder wall, etc., which can result in power losses. Therefore, how to reduce the power loss caused by these friction factors is one of the important issues to improve the efficiency of the compressor.

SUMMERY OF THE UTILITY MODEL

The present invention is directed to solving, at least to some extent, one of the technical problems presented in the related art. Therefore, the utility model provides a pump body assembly which can reduce power loss caused by friction to a certain extent.

In addition, the utility model also provides a rotary compressor with the pump body assembly.

In addition, the utility model also provides refrigeration equipment with the rotary compressor.

According to an embodiment of the first aspect of the utility model, the pump body assembly comprises:

a crankshaft including a first shaft portion, an eccentric portion, and a second shaft portion connected in sequence;

a first bearing connected to the first shaft portion;

a second bearing connected to the second shaft portion;

the roller is arranged on the eccentric part, two end surfaces of the roller are respectively connected with the inner surfaces of the first bearing and the second bearing in a sliding fit manner, and the inner circumferential surface of the roller is connected with the outer circumferential surface of the eccentric part in a sliding fit manner;

wherein one of the first bearing and the second bearing is located on an exhaust side of the pump block assembly, and the roller is provided with a notch portion on the end surface away from the exhaust side.

The pump body assembly according to the first aspect of the utility model has at least the following advantages: the notch part is arranged on the end surface of the roller, so that the sealing matching area formed between the end surface and the first bearing or the second bearing matched with the end surface is reduced, the friction power loss between the end surface and the first bearing or the second bearing can be reduced to a certain degree, and the efficiency of the compressor is effectively improved. In addition, because the notch part is arranged at the non-exhaust end, the risk of gas leakage caused by weakened sealing is avoided.

According to some embodiments of the utility model, the notch portion is formed by chamfering between the end face and the inner peripheral surface.

According to some embodiments of the utility model, with the width of the projection plane of the chamfer on the end surface as T and the wall thickness of the roller as T, the following conditions are satisfied: 1/3T < T < 1/2T.

According to some embodiments of the utility model, with an included angle θ between the chamfer and the end face, the following is satisfied: 0 < theta <30 deg..

According to some embodiments of the present invention, the roller is provided with a groove portion sinking in a radial direction of the roller at the inner peripheral surface at an end close to the exhaust side, and with a radius of the groove portion being r1 and a radius of an outer contour of the chamfer being r2, it is satisfied that: r1 < r 2.

According to some embodiments of the present invention, with a depth h of the groove portion in the roller axial direction, it suffices that: h is more than 0.5mm and less than 5 mm.

According to some embodiments of the present invention, with the depth of the groove portion in the axial direction of the roller being H, the eccentric portion is provided with a holding portion at one end close to the exhaust side, the holding portion matching the depth H of the groove portion, and with the maximum depth of the chamfer being H, the following is satisfied: h is less than H.

According to some embodiments of the utility model, the holding portion includes a flange formed on an outer circumferential surface of the eccentric portion.

According to some embodiments of the utility model, the flange is extended at a set length on a side of the eccentric portion adjacent to the first shaft portion or the second shaft portion.

The rotary compressor according to the second aspect embodiment of the present invention comprises the pump body assembly of the first aspect embodiment.

According to the third aspect embodiment of the utility model, the refrigeration equipment comprises the rotary compressor of the second aspect embodiment.

Additional aspects and advantages of the utility model will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the utility model.

Drawings

The utility model is further described with reference to the following figures and examples, in which:

fig. 1 is a schematic structural view of a pump body assembly according to an embodiment of the present invention, in which a first bearing is omitted.

Figure 2 is an exploded view of the pump body assembly of the embodiment of figure 1.

FIG. 3 is a schematic cross-sectional view of one orientation of the pump block assembly of the embodiment of FIG. 1.

FIG. 4 is a schematic cross-sectional view of the rollers in the pump block assembly of the embodiment of FIG. 1.

Fig. 5 is an enlarged schematic view at a in fig. 2.

Fig. 6 is an enlarged schematic view at B in fig. 3.

FIG. 7 is a schematic view of the pump block assembly of the embodiment of FIG. 1 with the rollers reversed.

Fig. 8 is a schematic structural view of a rotary compressor according to an embodiment of the present invention.

Reference numerals:

the pump body assembly comprises a pump body assembly 100, a crankshaft 110, a first shaft part 111, an eccentric part 112, a second shaft part 113, a butting part 114, a flange 115, a first bearing 120, a second bearing 130, a roller 140, an inner circumferential surface 141, an end surface 142, a notch part 143, a conical surface 144, a groove part 145, a cylinder 150, a working chamber 160, a slide sheet 170 and a spring 180;

the rotary compressor comprises a rotary compressor 200, a cylinder 211, an upper cover 212, a lower cover 213, an oil pool 214, an air outlet 215, a stator 221, a rotor 222, a liquid storage tank 230 and an air return port 231.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.

In the description of the present invention, it should be understood that the orientation or positional relationship referred to, for example, the upper, lower, etc., is indicated based on the orientation or positional relationship shown in the drawings, and is only for convenience of description and simplification of description, but does not indicate or imply that the device or element referred to must have a specific orientation, be constructed in a specific orientation, and be operated, and thus should not be construed as limiting the present invention.

In the description of the present invention, a plurality means two or more. If the first and second are described for the purpose of distinguishing technical features, they are not to be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.

In the description of the present invention, unless otherwise explicitly limited, terms such as arrangement, installation, connection and the like should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above terms in the present invention in combination with the specific contents of the technical solutions.

It is understood that the pump body assembly 100 provided by the present embodiment can be used in a rotary compressor 200 used in a refrigeration device such as an air conditioner, a refrigerator, etc., and a device for compressing gas in a rotary manner, such as an air compressor, used in various industrial fields such as petroleum, electric power, chemical industry, metallurgy, etc.

It can be understood that in the pump body assembly 100 of the rotary compressor 200, the roller performs a function of compressing gas by causing a volume change in the cylinder by rotating in the cylinder (revolving around the central axis of the crankshaft), and thus, it is necessary to secure a sealing engagement with the cylinder. In the related art, the roller is ensured to be in sealing fit connection with the cylinder and the bearing through size design and installation. In the pump block assembly 100, an upper bearing and a lower bearing (flange), a roller, and the like are assembled with the cylinder, so that the upper opening and the lower opening of the cylinder are closed by the two bearings to form a working chamber, and the roller is positioned in the working chamber and can be rotated by the crankshaft. When the pump block assembly 100 is operated, there is relative movement between the roller and the plurality of components, including relative sliding (rotation) between the inner peripheral surface of the roller and the eccentric portion, relative sliding between the upper end surface of the roller and the inner surface of the first bearing, relative sliding between the lower end surface of the roller and the inner surface of the second bearing, rolling between the outer surface of the roller and the cylinder wall, and the like. Sliding friction between the different interfaces generates power losses. In the related art, power loss due to sliding friction is reduced by improvement of a lubrication system.

It will also be appreciated that for the pump block assembly 100, the working chamber has an inlet port and an outlet port, wherein the inlet port is typically located in the cylinder wall and the outlet port is located at the edge of the inner face of the bearing on one side (or the cylinder wall and bearing have exhaust structure at the intersection at the same time) to allow for different directions of exhaust, such as up or down exhaust, whereby the exhaust side of the pump block assembly 100 is on the side of one of the two bearings.

Fig. 1 is a schematic structural view of a pump body assembly according to an embodiment of the present invention, fig. 2 is an exploded schematic view of the pump body assembly according to the embodiment of fig. 1, and fig. 3 is a sectional view of the pump body assembly according to the embodiment of fig. 1, and in conjunction with fig. 1 to 3, the pump body assembly 100 according to the embodiment includes a crankshaft 110, a first bearing 120 (refer to fig. 7), a second bearing 130, and a roller 140. Specifically, the crankshaft 110 includes a first shaft portion 111, an eccentric portion 112, and a second shaft portion 113 connected in this order, the first bearing 120 is connected to the first shaft portion 111, and the second bearing 130 is connected to the second shaft portion 113; the roller 140 is mounted on the eccentric portion 112, two end surfaces 142 of the roller 140 are respectively connected with the inner surfaces of the first bearing 120 and the second bearing 130 in a sliding fit manner, and the inner circumferential surface 141 of the roller 140 is connected with the outer circumferential surface of the eccentric portion 112 in a sliding fit manner. The side where the first bearing 120 is located is the exhaust side P of the pump block assembly 100, and the roller 140 is provided with a notch 143 on an end surface 142 away from the exhaust side P.

Accordingly, by providing the notch 143 on the end surface 142 of the roller 140, the sealing engagement area formed between the end surface 142 and the first bearing 120 or the second bearing 130 engaged therewith is reduced, and therefore, the friction power loss therebetween can be reduced to some extent, thereby effectively improving the efficiency of the compressor. Further, since the notch 143 is provided at the non-exhaust end, the risk of gas leakage due to the weakened seal is avoided.

Specifically, the pump block assembly 100 employs upper exhaust on the side where the non-exhaust side F of the pump block assembly 100 is disposed on the first bearing 120, i.e., in the direction of the drawing. A notched portion 143 is provided on an end surface 142 of the bottom portion of the roller 140, that is, the non-exhaust side F, a gap is formed between the area of the notched portion 143 of the roller 140 and the inner surface of the second bearing 130, and the two are not in contact with each other, and the end surface 142 forms a seal sliding fit connection only between the area of the non-notched portion 143 and the bearing, whereby a seal fit area can be reduced, thereby reducing a friction power loss at the cover surface.

It should be noted that, the inner surfaces of the first bearing 120 and the second bearing 130 described herein refer to the surfaces of the first bearing 120 and the second bearing 130 facing the working chamber 160 after being connected to the cylinder 150, that is, the surfaces that are in sliding fit with the end surfaces 142 of the rollers 140.

It can be understood that, since the exhaust port and the like are provided at the exhaust side P, if the notch 143 is also provided at the end surface 142 of the roller 140 on the exhaust side P side, when the roller 140 rotates to the position where the exhaust port is located, there is a risk of gas leakage between the exhaust port and the notch 143 due to an insufficient sealing distance, resulting in a decrease in the efficiency of the compressor. In the exhaust side P of the pump block assembly 100 of the present embodiment, since the end surface 142 of the roller 140 is not provided with the corresponding notched portion 143, it is possible to ensure effective sealing between the roller 140 at that end and the mating first bearing 120.

It is understood that the notch 143 provided on the end surface 142 of the roller 140 in the present embodiment may be formed in various configurations by removing material from the end surface 142, and such configurations may be continuous or intermittent, and may be partially configured on a partial region of the end surface 142. In short, as long as such a configuration can reduce the contact area between the end surface 142 and the inner surface of the second bearing 130, for example, the notch 143 may be a spot facing, an annular groove, a chamfer, or the like formed along the end surface 142.

It should be noted that the notch 143 described herein should not be understood as extending from the end face 142 of the roller 140 to the outer peripheral wall of the roller 140, otherwise, a gap may exist between the roller 140 and the wall of the cylinder 150, which may cause gas leakage, and affect the efficiency of the pump block assembly 100.

Referring to fig. 2, in some embodiments, the crankshaft 110 of the pump body assembly 100 includes a first shaft portion 111, an eccentric portion 112, and a second shaft portion 113, which are sequentially connected. The first shaft 111 is a long shaft, and the second shaft is a short shaft. The upper end of the first shaft portion 111 is used to connect with a rotor of a motor of the compressor, and the motor transmits power to the first shaft portion 111 in a torque manner so that the crankshaft 110 can rotate. During the rotation of the crankshaft 110, the eccentric portion 112 of the crankshaft rotates the roller 140. It is understood that the rollers 140 revolve around the central axis of the crankshaft 110 while rotating around the central axis of the eccentric portion 112. Further, inside the crankshaft 110, there is a deep hole extending in the axial direction thereof for delivering the lubricating oil in the compressor bottom oil sump 214 to each moving part of the pump body assembly 100, whereby an oil film is formed by the lubricating oil between the interfaces of the relatively moving parts, to improve the efficiency and reliability of the compressor with less frictional resistance.

In addition, referring to fig. 1 to 3, the pump body assembly 100 further includes a cylinder 150, and the cylinder 150 is in an approximately circular cylinder shape and has an upper opening and a lower opening. The first bearing 120 and the second bearing 130 are coupled to the top and bottom of the cylinder 150, respectively, to form a working chamber 160 for compressed gas. A vane 170 is provided in the cylinder 150, and the vane 170 is elastically supported against the outer circumferential surface of the roller 140 by an elastic member such as a spring 180, thereby being reciprocated by the rotation of the roller 140 to divide the working chamber 160 into a high pressure chamber and a low pressure chamber.

In some embodiments, the first bearing 120 and the second bearing 130 of the pump block assembly 100 are used, on the one hand, to connect with the cylinder 150 to form the working chamber 160 and, on the other hand, to support and position the first shaft portion 111 and the second shaft portion 113 of the crankshaft 110. The first bearing 120 and the second bearing 130 are both integrally flange-like disk-shaped parts and have receiving holes for slidably fitting with the crankshaft 110, wherein the first bearing 120 is slidably fitted with the first shaft portion 111 of the crankshaft 110, and the second bearing 130 is slidably fitted with the second shaft portion 113 of the crankshaft 110, whereby the crankshaft 110 can correctly transmit force and motion by the support and positioning of the first bearing 120 and the second bearing 130 when the crankshaft 110 is driven to rotate by the motor.

Fig. 4 is a schematic cross-sectional view of a roller in the pump block assembly of the embodiment of fig. 1, and referring to fig. 2 and 3 in conjunction with fig. 4, in some embodiments, the roller 140 of the pump block assembly 100 is in the shape of a circular sleeve having an inner circumferential surface 141 that mates with the eccentric portion 112, and end surfaces 142 at both ends. Which is continuously rotated in the working chamber 160 of the cylinder 150 by the rotation of the crankshaft 110, resulting in a change in the volume of the working chamber 160, thereby compressing gas to perform work.

It is conceivable that the above-mentioned parts should ensure dimensional accuracy of installation and a smooth working surface in order to increase the efficiency of the compressor as much as possible and reduce gas leakage.

It is also understood that although the crankshaft 110 has been described as having an eccentric portion 112, the pump body assembly 100 of the present embodiment may be used in a two-cylinder or multi-cylinder compressor. For example, in a two-cylinder or multi-cylinder compressor, the crankshaft 110 has two or more eccentric portions 112, and the cylinder block also has a corresponding number of working chambers 160, and the two adjacent working chambers 160 are separated by a partition, so that the partition for separating the two working chambers 160 can be used as the first bearing 120 or the second bearing 130 in the pump body assembly 100 of the present embodiment.

Referring to fig. 3 and 4, in order to be able to machine the notch 143 in a simple manner, in some embodiments, the notch 143 is formed by chamfering between the end surface 142 and the inner circumferential surface 141. Specifically, an annular tapered surface 144 is formed on the end surface 142 of the roller 140. Therefore, the convenience and the economy of processing can be effectively improved. Meanwhile, the notch 143 in the form of a chamfer can reduce the contact area between the inner circumferential surface 141 of the roller 140 and the eccentric portion 112 of the crankshaft 110 by extending the notch 143 to the inner circumferential surface 141 of the roller 140, thereby reducing the friction power loss therebetween and further improving the operating efficiency of the compressor.

Further, in order to effectively ensure the effect of the chamfered notch 143, the projection surface shape is annular with the width of the projection surface of the chamfer on the end surface being T, and therefore, the width of the ring is the width of the projection surface, and the wall thickness of the roller 140 is T, satisfying: 1/3T < T <1/2T, and further, the included angle between the chamfered tapered surface 144 and the end surface 142 is θ, which satisfies: 0 < theta <30 deg.. It will be appreciated that the provision of the notch 143 in the form of a chamfer increases the clearance volume of the pump block assembly 100, which theoretically results in a loss of cooling capacity of the compressor, but the efficiency of the compressor is improved to some extent according to the empirical formula described above.

With continued reference to fig. 4, in some embodiments, the inner circumferential surface 141 of the roller 140 at an end near the exhaust side P is provided with a groove portion 145 sinking in a radial direction of the roller 140, whereby the groove portion 145 has an inner circumferential surface such that a radius of the groove portion 145 is r1 and a radius of an outer contour of the chamfer is r2, satisfying: r1 < r 2. It is understood that, in order to avoid the adverse effect of the notch 143 on the exhaust side P, the groove 145 should have a smaller size to ensure the sealing performance between the end surface 142 of the roller 140 and the first bearing 120. Accordingly, the groove 145 reduces the contact area between the inner circumferential surface 141 of the roller 140 and the eccentric portion 112 of the crankshaft 110, thereby reducing the frictional power loss therebetween and further improving the operating efficiency of the compressor.

In order to further improve the efficiency of the compressor, the depth of the groove portion 145 in the axial direction of the roller 140 is h, which satisfies: h is more than 0.5mm and less than 5 mm. It will be appreciated that the provision of the slot 145 increases the clearance volume of the pump block assembly 100, which theoretically results in a loss of cooling capacity of the compressor, but the efficiency of the compressor is improved to some extent according to the empirical formula described above.

It can be understood that, for the purpose of improving the efficiency of the compressor, the pump body assembly 100 of the present embodiment is provided with the notch 143 at the end surface 142 of the roller 140 close to the discharge side P, so that if the roller 140 is assembled in a wrong direction, gas leakage may be caused, and the performance of the compressor may be seriously affected.

For example, the maximum outer contour radius of the openable chamfer is set to r0 on the end surface 142 of the roller 140 near the exhaust side P, and if r2 exceeds this dimension, when the roller 140 is rotated to the exhaust port position, the sealing distance from the exhaust port becomes insufficient, and leakage occurs. Therefore, in order to avoid a risk of gas leakage that may occur, the notch 143, i.e., the chamfer, may be located on the non-exhaust side F by setting r2 to be not more than r0, or by ensuring that the mounting direction of the roller 140 is correct at the time of assembly. It is understood that, in the above measures, if r2 is set smaller than r0, the effect of reducing the friction power loss by the notch 143 is limited, and if r2 is set larger, the risk of the assembly link is increased, and the cost is also increased.

Fig. 5 is an enlarged schematic view at a in fig. 2, and with reference to fig. 4 and 5, in some embodiments, in order to reduce the contact area between the end face 142 where the chamfer is located and the first bearing 120 or the second bearing 130 and reduce the risk of gas leakage due to misassembly by increasing the radius of the outer contour of the chamfer to r2 as much as possible, the depth of the groove portion 145 in the axial direction of the roller 140 is H, the end of the eccentric portion 112 near the exhaust side P is provided with an abutting portion 114 matching the depth H of the groove portion 145, and the maximum depth of the tapered surface 144 of the chamfer is H, which satisfies: h is less than H.

Fig. 6 is an enlarged schematic view at B in fig. 3, showing a state where the roller 140 is correctly mounted to the eccentric portion 112, and in connection with fig. 6, it can be understood that, when the assembly of the roller 140 is performed, if the roller 140 is mounted in the correct direction, the abutting portion 114 can be completely received by the groove portion 145 and the roller 140 can be normally mounted in place.

Fig. 7 is a schematic view of the pump body assembly 100 of fig. 1 in a state that the roller 140 is reversely mounted, and with reference to fig. 7, if the roller 140 is mounted in a wrong direction, the chamfer surface 144 has a smaller depth at the edge, and the chamfer surface 144 interferes with the abutting portion 114, so that the roller cannot be completely mounted, and meanwhile, it can be found that the mounting direction of the roller 140 is wrong, i.e. timely adjustment can be performed, so as to ensure that the roller 140 can be mounted in a correct direction.

It can be understood that, because the risk of misassembly is avoided, the outer contour radius of the chamfer is designed to be larger than r0, which is larger than r2, so that the efficiency of the compressor can be effectively improved. Of course, the radius r1 of the groove portion 145 on the exhaust side is set to be not more than r0 to ensure the sealing effect of the roller 140 on that side.

The inventor verifies through experiments that the efficiency of the compressor can be improved to a certain extent through the improvement. The details can be seen in the following table:

wherein the power in the table refers to the power consumed by the pump body assembly 100.

As can be seen from the above table, both Of the compressor types 1 and 2 exhibit an improvement in the Coefficient Of Performance Of the Compressor (COP), that is, the energy efficiency Of the compressor. Therefore, through the matching of the large-sized notch 143, the small-sized groove 145 and the abutting portion 114 on the eccentric portion 112 of the crankshaft 110, the pump body assembly 100 of the present embodiment has the characteristic of high manufacturability while improving the efficiency of the compressor.

With continued reference to fig. 5, in some embodiments, the abutting portion 114 includes a flange 115 formed on the outer circumferential surface of the eccentric portion 112, and the flange 115 may be simultaneously formed during the machining of the crankshaft 110 to effectively ensure the positional and dimensional accuracy thereof. It is to be understood that the cross-sectional shape of the flange 115 is not particularly limited as long as it can function as the notch 143 of the interference roller 140, and for example, the cross-sectional shape of the flange 115 may be a trapezoidal boss as shown in fig. 6 and 7, and may also be other shapes such as a rectangular boss, a circular-arc boss, or a ratchet shape.

Further, in some embodiments, referring to fig. 5, the flange 115 is provided to extend at a set length on a side of the eccentric portion 112 adjacent to the first shaft portion 111 or the second shaft portion 113. That is, the flange 115 is formed on the outer circumferential surface of the eccentric portion 112 in the form of a circular arc segment, and the circular arc segment is disposed on the eccentric portion 112 in the vicinity of the central axis of the crankshaft 110 (i.e., the common rotational axis of the first shaft portion 111 or the second shaft portion 113), whereby the flange 115 is very convenient to machine and form, and the length to be machined is small, and the manufacturing cost can be reduced, and further, the thickness of the remaining region of the eccentric portion 112 away from the first shaft portion 111 can be reduced, the weight thereof can be reduced, which is advantageous in reducing the moment of inertia of the crankshaft 110, facilitating the motion control, and also in optimizing the vibration when the crankshaft moves. It is to be understood that the extending length of the flange 115 is not particularly limited, and the length may be set according to actual needs, provided that the conditions such as the economical efficiency of processing are satisfied.

The pump body assembly 100 of the above embodiment may be used in the rotary compressor 200. For example, the rotary compressor 200 according to the second aspect of the present invention may include the pump body assembly 100 of the above embodiment. By using the pump body assembly 100 of the above embodiment, the efficiency of the rotary compressor 200 of the present embodiment can be improved to some extent.

Fig. 8 is a schematic structural view illustrating a rotary compressor according to an embodiment of the present invention, and as shown in fig. 8, the rotary compressor 200 includes a housing, a pump body assembly 100, a motor assembly, a reservoir 230, and other components, in some embodiments. The housing includes a cylinder 211, an upper cover 212, and a lower cover 213. The cylinder 211 is axially penetrated. The upper cover 212 is provided at an upper portion of the cylinder 211 and is fixed to the upper portion of the cylinder 211 by means of, for example, welding. The lower cover 213 is provided at a lower portion of the cylinder 211 and is fixed to the lower portion of the cylinder 211 by means of, for example, welding. Thus, the cylindrical body 211, the upper cover 212, and the lower cover 213 form a sealed installation space. The pump body assembly 100, the motor assembly, and the like are respectively installed in the installation space. The lower cover 213 of the housing is recessed downward, whereby an oil sump 214 for storing lubricating oil is formed at the bottom of the housing. At the top of the housing, there is an air outlet 215.

The accumulator 230 is connected to the housing, and the accumulator 230 has an external return port 231 for separating the refrigerant from the vapor and liquid to deliver the refrigerant in a gaseous state into the pump assembly 100 for compression.

The motor assembly includes a stator 221 and a rotor 222. The stator is fixed to, for example, an inner wall surface of the cylindrical body 211 of the housing, and the rotor 222 is located in the middle of the stator 221. The first shaft portion 111 of the crankshaft 110 passes through a shaft hole in the middle of the rotor 222 and is fixed to the rotor 222. When the rotary compressor 200 is energized, the stator 221 rotates the rotor 222, and the crankshaft 110 rotates with the rotation of the rotor 222.

The rotary compressor 200 of the above embodiment may be used in a refrigeration apparatus. For example, the refrigeration apparatus according to the third aspect of the present invention may include a rotary compressor 200. By using the rotary compressor 200 of the above embodiment, the efficiency of the refrigeration apparatus can be improved.

The embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge of those skilled in the art without departing from the gist of the present invention.

Claims (11)

1. Pump body subassembly, its characterized in that includes:

a crankshaft including a first shaft portion, an eccentric portion, and a second shaft portion connected in sequence;

a first bearing connected to the first shaft portion;

a second bearing connected to the second shaft portion;

the roller is arranged on the eccentric part, two end surfaces of the roller are respectively connected with the inner surfaces of the first bearing and the second bearing in a sliding fit manner, and the inner circumferential surface of the roller is connected with the outer circumferential surface of the eccentric part in a sliding fit manner;

wherein one of the first bearing and the second bearing is located on an exhaust side of the pump block assembly, and the roller is provided with a notch portion on the end surface away from the exhaust side.

2. The pump body assembly according to claim 1, wherein the notch portion is formed by chamfering between the end face and the inner peripheral surface.

3. The pump body assembly according to claim 2, wherein, with a width T of a projection plane of the chamfer on the end face and a wall thickness T of the roller, a condition is satisfied: 1/3T < T < 1/2T.

4. The pump body assembly according to claim 2, wherein an included angle θ between the chamfer and the end face satisfies: 0 < theta <30 deg..

5. The pump body assembly according to any one of claims 2 to 4, wherein the inner peripheral surface of the roller at an end close to the exhaust side is provided with a groove portion that sinks in a radial direction of the roller, and with a radius of the groove portion being r1, an outer profile radius of the chamfer being r2, satisfying: r1 < r 2.

6. The pump body assembly according to claim 5, wherein with a depth h of the groove portion in the roller axial direction, it suffices: h is more than 0.5mm and less than 5 mm.

7. The pump body assembly according to claim 5, wherein the depth of the groove portion in the axial direction of the roller is H, the eccentric portion is provided with a holding portion matching the depth H of the groove portion at one end close to the exhaust side, and the maximum depth of the chamfer is H, so that: h is less than H.

8. The pump body assembly of claim 7, wherein the retention portion includes a flange formed on an outer peripheral surface of the eccentric portion.

9. The pump body assembly of claim 8, wherein the flange extends a set length on a side of the eccentric portion proximate the first or second shaft portions.

10. Rotary compressor, characterized in that it comprises a pump body assembly according to any one of claims 1 to 9.

11. A refrigerating apparatus comprising the rotary compressor of claim 10.

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