CN216589109U

CN216589109U - Pump body structure, compressor and air conditioner

Info

Publication number: CN216589109U
Application number: CN202123022470.2U
Authority: CN
Inventors: 魏会军; 徐嘉; 余冰; 杨欧翔; 赵海红
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2021-12-03
Filing date: 2021-12-03
Publication date: 2022-05-24
Anticipated expiration: 2031-12-03

Abstract

The utility model discloses a pump body structure, a compressor and an air conditioner, wherein the pump body structure comprises a lubricating structure, the inlet end of the lubricating structure is communicated with an oil supply hole on a crankshaft, and the outlet end of the lubricating structure is communicated with a gap between a sliding vane and a sliding chute; the lubricating structure comprises an axial oil groove arranged on the wall of the sliding groove of the air cylinder component, and the flow sectional area of the axial oil groove is smaller than that of the oil supply hole. The lubricating oil is divided into two paths for lubrication through the oil supply hole, one path provides lubrication for the gap through the lubricating structure, and the other path provides lubrication for the short shaft part of the crankshaft through the bearing oil groove; because the flow cross-sectional area of the axial oil groove is limited to be smaller than that of the oil supply hole, the axial oil groove and the bearing oil groove can obtain sufficient lubricating oil flow, the lubricating oil of the axial oil groove reaches a certain axial flow speed, bubble-shaped gaseous refrigerant generated by heat generation due to friction can be quickly taken away, and the problem of increasing sliding vane gap leakage caused by gaseous refrigerant aggregation is solved.

Description

Pump body structure, compressor and air conditioner

Technical Field

The utility model relates to the technical field of compressors, in particular to a pump body structure, a compressor and an air conditioner.

Background

The compressor is widely applied to refrigeration systems such as air conditioners, heat pumps, freezing and refrigerating systems and the like, and the performance level of the compressor is a key factor influencing the performance of related refrigeration products. The rolling piston compressor has the advantages that the pump body mainly comprises a cylinder, a crankshaft, a piston, a slip sheet, a bearing and other parts, the cylindrical piston makes eccentric rotation motion along with the crankshaft, the outer wall of the piston and the inner wall of the cylinder form a crescent working cavity, the slip sheet in a sliding groove of the cylinder is abutted to the outer wall of the piston, the crescent working cavity is divided into an air suction cavity and a compression cavity, the volumes of the air suction cavity and the compression cavity are periodically changed along with the rotation of the crankshaft, and therefore the working processes of air suction, compression, exhaust and the like are achieved. In the process, the sliding sheet reciprocates in the sliding groove, and the part of the sliding sheet extending into the inner wall of the cylinder is under the action of the air suction cavity and the compression cavity, so that large extrusion force exists between the sliding sheet and the sliding groove, and the friction power consumption of the sliding sheet is large.

In order to solve the above problems, the related art adopts the following scheme: the oil pump provides positive pressure to enable the lubricating oil to fill the vertical oil channel adjacent to the side face of the sliding sheet, so that the effect of improving the lubrication is achieved; however, with the development of lightweight of the compressor, the initial oil injection amount in the compressor is reduced, the oil level is reduced, and the total amount of pump oil is reduced, but the above scheme does not limit the amount of lubricating oil used for improving sliding vane friction, so that more lubricating oil is often filled in the vertical oil passage, and under the condition that the initial oil injection amount in the compressor is reduced, the oil supply on the short shaft of the crankshaft is insufficient, and the friction power consumption and the abrasion of the crankshaft of the compressor are aggravated by the uneven oil supply mode.

SUMMERY OF THE UTILITY MODEL

In view of this, the present invention provides a pump body structure, a compressor and an air conditioner, in which the size of the flow cross-sectional areas of an axial oil groove for sliding vane friction and an oil supply hole is limited, so that the oil supply hole reasonably distributes the oil flow rates of the axial oil groove and a crankshaft short shaft, and simultaneously satisfies the lubrication requirements of the axial oil groove and the crankshaft short shaft, and avoids the problem of friction power consumption increase caused by uneven oil supply.

In order to solve the above problems, according to an aspect of the present application, an embodiment of the present invention provides a pump body structure for a compressor, the pump body structure including a lubricating structure, an inlet end of the lubricating structure communicating with an oil supply hole on a crankshaft of the compressor, and an outlet end communicating with a gap between a vane and a sliding groove of the compressor;

the pump body structure further comprises an air cylinder assembly, the lubricating structure comprises an axial oil groove formed in the sliding groove wall of the air cylinder assembly, and the flow sectional area of the axial oil groove is smaller than that of the oil supply hole.

In some embodiments, the axial oil groove has a cross-sectional flow area greater than the cross-sectional flow area of the gap.

In some embodiments, the axial oil groove has a cross-sectional flow area and the oil supply hole has a cross-sectional flow area that satisfies: S/S1 is less than 0.8; s is the flow cross-sectional area of the axial oil groove, and S1 is the flow cross-sectional area of the oil supply hole.

In some embodiments, the axial oil groove has a cross-sectional flow area and the gap has a cross-sectional flow area that satisfies: S/S2 is more than 1.5; s is the flow cross-sectional area of the axial oil groove, and S2 is the flow cross-sectional area of the gap.

In some embodiments, the axial oil groove divides the sealing surface of the slide and the slide into a first sealing surface and a second sealing surface, the first sealing surface and the second sealing surface having a width that satisfies: 0.4 < (L1+ L2)/L < 1; wherein, L1 is the width of first sealed face, and L2 is the width of second sealed face, and L is the distance between the hole of dodging of compressor and the cylinder assembly inner wall.

In some embodiments, the first and second sealing surfaces have a width that satisfies: 0.6 < (L1+ L2)/L < 0.9.

In some embodiments, the wall of the chute is connected to the axial groove by a transition section, the transition section being a curve, the tangent to the curve at the end point and the wall of the chute forming an obtuse angle.

In some embodiments, the cylinder assembly comprises at least one cylinder.

In some embodiments, when the cylinder assembly comprises a cylinder, the lubricating structure further comprises a radial channel which is opened in the lower bearing of the pump body structure and is communicated with the axial oil groove, one end of the radial channel is communicated with the oil supply hole through the annular groove, and the other end of the radial channel is provided with a plug.

In some embodiments, the lubricating structure further comprises a second axial oil groove, an inlet end of the second axial oil groove is communicated with the axial oil groove through the discharge groove, and an outlet end is communicated with the avoidance hole.

In some embodiments, the axial oil grooves and/or the radial channels are arranged obliquely such that the included angle between the two is an obtuse angle.

In some embodiments, when the cylinder assembly comprises two cylinders, the two cylinders are an upper cylinder and a lower cylinder respectively, the cylinder assembly further comprises a middle partition plate arranged between the upper cylinder and the lower cylinder, and the axial oil groove is formed in the sliding groove wall of the upper cylinder; the cylinder assembly further comprises a second upper bearing arranged on the upper end face of the upper cylinder and a second lower bearing arranged on the lower end face of the lower cylinder.

In some embodiments, the lubricating structure further comprises a third axial oil groove formed in the wall of the sliding groove of the lower cylinder and a second radial channel formed in the middle partition plate, one end of the second radial channel is communicated with the inner cavity of the middle partition plate, the other end of the second radial channel is provided with a second plug, one end of the axial oil groove is communicated with the second radial channel, the other end of the axial oil groove is communicated with the upper discharge groove, one end of the third axial oil groove is communicated with the second radial channel, and the other end of the third axial oil groove is communicated with the lower discharge groove.

In some embodiments, the upper discharge groove is formed in the upper end surface of the upper cylinder, and the lower discharge groove is formed in the lower end surface of the lower cylinder.

In some embodiments, the upper drain groove opens at a lower end surface of the second upper bearing, and the lower drain groove opens at an upper end surface of the second lower bearing.

In some embodiments, the axial oil groove penetrates the chute wall of the upper cylinder, the middle partition plate, and the chute wall of the lower cylinder.

According to another aspect of the present application, an embodiment of the present invention provides a compressor including the pump body structure described above.

According to another aspect of the present application, an embodiment of the present invention provides an air conditioner including the compressor described above.

Compared with the prior art, the pump body structure at least has the following beneficial effects:

lubricating oil is divided into two paths for lubrication through an oil supply hole of the crankshaft, wherein one path reaches a gap between the sliding vane and the sliding chute through a lubricating structure to provide lubrication for the movement of the sliding vane, and the other path provides lubrication for a short shaft part of the crankshaft through a bearing oil groove; because the flow cross-sectional area of the axial oil groove is limited to be smaller than that of the oil supply hole, the axial oil groove and the bearing oil groove can obtain sufficient lubricating oil flow, the lubricating oil of the axial oil groove reaches a certain axial flow speed, bubble-shaped gaseous refrigerant generated by heat generation due to friction can be quickly taken away, and the problem of increasing sliding vane gap leakage caused by gaseous refrigerant aggregation is solved.

On the other hand, the compressor provided by the present invention is designed based on the pump body structure, and the beneficial effects thereof refer to the beneficial effects of the pump body structure, which are not described herein again.

On the other hand, the air conditioner provided by the present invention is designed based on the above compressor, and the beneficial effects thereof refer to the beneficial effects of the above compressor, which are not repeated herein.

The foregoing description is only an overview of the technical solutions of the present invention, and in order to make the technical solutions of the present invention more clearly understood and to implement them in accordance with the contents of the description, the following detailed description is given with reference to the preferred embodiments of the present invention and the accompanying drawings.

Drawings

FIG. 1 is a cross-sectional view of a pump body structure provided by an embodiment of the present invention;

FIG. 2 is a sectional view taken along line A-A of FIG. 1;

FIG. 3 is an enlarged view of a portion of FIG. 2 at A;

FIG. 4 is a view of the axial oil groove and vane arrangement of a pump body structure according to an embodiment of the present invention;

FIG. 5 is a cross-sectional layout view of a pump body structure provided by an embodiment of the present invention;

FIG. 6 is a cross-sectional view of a pump block structure when axial oil grooves and radial passages are obliquely arranged according to an embodiment of the present invention;

FIG. 7 is a partial cross-sectional view of another pump body structure provided by an embodiment of the present invention;

FIG. 8 is a partial cross-sectional view of another pump body structure provided by an embodiment of the present invention;

FIG. 9 is a cross-sectional view of a pump block assembly when the cylinder assembly includes two cylinders in a pump block structure according to an embodiment of the present invention;

FIG. 10 is a cross-sectional view of another pump block assembly in a pump block configuration provided by an embodiment of the present invention when the cylinder assembly includes two cylinders;

FIG. 11 is a graph of relative COP as a function of λ 1 for a pump body configuration according to an embodiment of the present invention;

FIG. 12 is a graph of relative COP as a function of λ 2 for a pump body configuration according to an embodiment of the present invention;

FIG. 13 is a graph of relative COP as a function of λ 3 for a pump body configuration according to an embodiment of the present invention.

Wherein:

1. a lubrication structure; 2. a crankshaft; 21. an oil supply hole; 3. sliding blades; 4. a chute; 5. a cylinder assembly; 6. avoiding holes; 7. a lower bearing; 11. an axial oil groove; 12. a radial channel; 13. a ring groove; 14. A plug; 15. a second axial oil groove; 16. a discharge tank; 51. an upper cylinder; 52. a lower cylinder; 53. A middle partition plate; 54. a second upper bearing; 55. a second lower bearing; 101. a third axial oil groove; 102. a second radial passage; 103. a second plug; 104. an upper drain tank; 105. a lower discharge tank; 111. a transition section.

Detailed Description

To further explain the technical means and effects of the present invention for achieving the intended purpose of the utility model, the following detailed description of the embodiments, structures, features and effects according to the present application will be given with reference to the accompanying drawings and preferred embodiments. In the following description, different "one embodiment" or "an embodiment" refers to not necessarily the same embodiment. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments.

In the description of the present invention, it is to be understood that the terms "vertical", "lateral", "longitudinal", "front", "rear", "left", "right", "upper", "lower", "horizontal", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description of the present invention, and do not mean that the device or member to which the present invention is directed must have a specific orientation or position, and thus, cannot be construed as limiting the present invention.

In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.

Example 1

The present embodiment provides a pump body structure, as shown in fig. 1 and fig. 2, the pump body structure is used for a compressor, and includes a lubricating structure 1, an inlet end of the lubricating structure 1 is communicated with an oil supply hole 21 on a compressor crankshaft 2, and an outlet end is communicated with a gap between a sliding vane 3 and a sliding chute 4 of the compressor; the pump body structure further comprises a cylinder assembly 5, the lubricating structure 1 comprises an axial oil groove 11 formed in the wall of a sliding groove of the cylinder assembly 5, and the flow sectional area of the axial oil groove 11 is smaller than that of the oil supply hole 21.

Specifically, the lubricating oil is divided into two paths for lubrication through an oil supply hole 21 of the crankshaft 2, wherein one path reaches a gap between the sliding vane 3 and the sliding chute 4 through the lubricating structure 1 to provide lubrication for the movement of the sliding vane 3, and the other path provides lubrication for a short shaft part of the crankshaft 2 through a bearing oil groove; because the flow cross-sectional area of the axial oil groove is limited to be smaller than that of the oil supply hole in the embodiment, the axial oil groove 11 and the bearing oil groove can obtain sufficient lubricating oil flow, the lubricating oil of the axial oil groove reaches a certain axial flow speed, the bubble-shaped gaseous refrigerant generated by frictional heat can be taken away quickly, and the problem of increasing the leakage of a sliding vane gap caused by the aggregation of the gaseous refrigerant is avoided.

In a specific embodiment:

the flow cross-sectional area of the axial oil groove 11 is larger than that of the gap; the flow cross-sectional area S2 of the gap is δ · Hc, where Hc is the height of the cylinder in the axial direction, and δ is the gap between the vane and the runner (as shown in fig. 4).

More specifically, the flow cross-sectional area of the axial oil groove 11 and the flow cross-sectional area of the oil supply hole 21 satisfy: S/S1 is less than 0.8; s is a flow cross-sectional area of the axial oil groove 11, and S1 is a flow cross-sectional area of the oil supply hole 21.

Let λ 1 be S/S1, the arrow in fig. 5 is the flowing direction of the lubricating oil, one path of the lubricating oil reaches the gap between the sliding vane 3 and the sliding groove 4 through the lubricating structure 1 to provide lubrication for the movement of the sliding vane 3, and the other path provides lubrication for the short shaft part of the crankshaft 2 through the bearing oil groove; because the axial oil groove 11 and the cylinder working cavity have larger pressure difference, the lubricating oil in the sliding groove 4 mainly flows out through the lubricating structure 1, and in order to avoid insufficient oil flow of the bearing oil groove, the ratio lambda 1 (namely S/S1) of the flow cross-sectional area S of the axial oil groove 11 to the flow cross-sectional area S1 of the oil supply hole 21 is set to be less than 0.8.

Fig. 11 also shows the relationship between the performance verification effect of the compressor and λ 1, and the neutral to COP is defined as the ratio of COP of the pump body structure using the present invention to COP of the conventional pump body structure, wherein COP refers to the ratio of the cooling capacity to the input power of the compressor, and the higher COP indicates the higher efficiency of the compressor; as can be seen from the graph, when λ 1 is less than 0.8, the relative COP is at a higher level; when λ 1 is greater than 0.8, the relative COP decreases rapidly. It can be seen that λ 1 plays a key role in the distribution of lubricating oil, and a reasonable λ 1 allows both the lubrication structure and the bearing structure to obtain sufficient flow of lubricating oil. Although increasing the oil supply amount of the ring groove by increasing the flow area of the oil supply hole is also helpful to solve the problem of uneven oil supply, the conventional method reduces the structural strength of the crankshaft, increases the circulation amount of oil, and causes the problems of increased oil discharge rate of the compressor, reduced reliability and the like.

In a specific embodiment:

the flow cross-sectional area of the axial oil groove 11 and the flow cross-sectional area of the gap satisfy: S/S2 is more than 1.5; s is a flow cross-sectional area of the axial oil groove 11, and S2 is a flow cross-sectional area of the clearance.

The height of the cylinder in the axial direction is Hc, and the clearance between the vane 3 and the runner 4 is δ, so that the flow cross-sectional area of the clearance, that is, the vane side clearance leakage passage area S2 becomes δ · Hc. The axial oil groove 11 has a flow cross-sectional area S, a ratio λ 2 of S/S2, λ 2> 1.5. Research discovers that the sliding vane 3 and the sliding chute 4 generate heat through friction to cause the refrigerant dissolved in the lubricating oil to be separated out in a bubble form, the viscosity of the lubricating oil with bubbles is reduced, the leakage speed of the side clearance of the sliding vane 3 is accelerated, the separation of the refrigerant is further aggravated for avoiding the quick reduction of the pressure of the axial oil groove 11, the ratio lambda 2 is set to be more than 1.5, and the stability of the oil supply pressure and the sufficient oil supply flow in the axial oil groove 11 can be ensured. In addition, the oil supply hole 21 includes one or more oil supply passages communicating the central oil hole of the crankshaft 2 with the slide groove 4.

Fig. 12 shows the relationship between the compressor performance verification effect and λ 2, and it can be seen from the graph that, relative to the COP which first rises rapidly with λ 2, after λ 2>1.5, it gradually becomes stable and remains at a higher level, and the COP maximum rise amplitude reaches 11%.

In a specific embodiment:

the axial oil groove 11 divides the sliding sheet 3 and the sealing surface of the sliding groove 4 into a first sealing surface and a second sealing surface, and the width of the first sealing surface and the width of the second sealing surface meet the following requirements: 0.4 < (L1+ L2)/L < 1; wherein, L1 is the width of the first sealing surface, L2 is the width of the second sealing surface, and L is the distance between the avoiding hole 6 of the compressor and the inner wall of the cylinder assembly 5.

Preferably, the width of the first sealing surface and the second sealing surface satisfies: 0.6 < (L1+ L2)/L < 0.9.

An avoiding hole 6 for avoiding a spring is formed in the outward side of the cylinder sliding groove 4, the distance between the avoiding hole 6 and the inner wall of the cylinder is L, the axial oil groove 11 at least divides the sealing surface of the sliding piece 3 and the sliding groove 4 into two parts, the widths of the two parts are L1 and L2 respectively, the ratio lambda 3 is (L1+ L2)/L, when lambda 3 is more than 0.4 and less than 1, the lubrication and the sealing of the sliding piece 3 can be improved, and particularly when lambda 3 is more than 0.6 and less than 0.9, the lubrication and the sealing effect are better. The reason is that the width of the sealing belt of the sliding vane 3 and the sliding chute 4 is too small when the lambda 3 is too small, even if the oil supply is sufficient, the leakage amount of the oil is still large, and the gas in the working cavity is overheated due to the fact that the oil has large specific heat and high temperature, and the compression power loss is increased; if lambda 3 is too large, the contact surface between the axial oil groove 11 and the sliding vane 3 is too small, the oil carrying capacity on the surface of the sliding vane 3 is insufficient, and the oil supply in the sliding vane gap is insufficient.

Fig. 13 shows the relationship between the performance verification effect of the pump body structure and λ 3, and it can be seen from the graph that the relative COP increases first and then decreases with the change of λ 3: when the lambda 3 is less than 0.4, the relative COP is less than 1, which shows that the lubrication structure causes the clearance seal of the sliding vane to be greatly deteriorated, the negative effect caused by leakage is greater than the positive effect caused by lubrication improvement, and the performance of the compressor is reduced; when the lambda 3 is more than 0.4 and less than 1, the relative COP is more than 1, which shows that the lubricating structure 1 has positive effect; when the lambda 3 is more than 0.6 and less than 0.9, the relative COP is more than 107 percent, and a remarkable effect-improving effect is achieved.

In a specific embodiment:

as shown in fig. 4, the chute wall is connected to the axial oil groove 11 through a transition section 111, the transition section is a curve, and an included angle between a tangent line of the curve at an end point and the chute wall is an obtuse angle.

Specifically, fig. 3 shows that the gap δ between the sliding vane 3 and the sliding groove 4 is formed by the gaps on both sides of the sliding vane 3, a transition section is provided between the axial oil groove 11 and the straight line segment of the sliding groove wall of the sliding groove 4, the transition section can be a straight line or a curve, but when the transition section is a curve, an included angle between a tangent line of the transition section and the straight line segment of the sliding groove wall is an obtuse angle, which is beneficial for the lubricating oil to enter the gap on the side surface of the sliding vane.

In addition, the lubricating structure 1 provided by the embodiment can be applied to a single-cylinder compressor and can also be applied to a parallel-bar compressor.

When the lubricating structure is applied to a single-cylinder compressor, the lubricating structure 1 further comprises a radial channel 12 which is arranged in the lower bearing 7 of the pump body structure and communicated with the axial oil groove 11, one end of the radial channel 12 is communicated with the oil supply hole 21 through the annular groove 13, and the other end of the radial channel is provided with a plug 14.

Specifically, as a preferred embodiment, the annular groove 13 is a circular cylindrical groove, the radial channel 12 is a circular hole perpendicular to the axis and penetrating through the inner wall and the outer wall of the lower bearing 7, a plug 14 is arranged on one side of the radial channel 12 close to the outer wall of the lower bearing 7, and the plug 14 and the radial channel 12 are fixed together by at least one of welding, threads, interference, bonding and the like.

The lubricating oil flowing out from the oil supply hole 12 flows into the clearance between the sliding vane 3 and the sliding groove 4 through the annular groove 13, the radial passage 12 and the axial oil groove 11 in sequence.

In a specific embodiment:

as shown in fig. 7 and 8, the lubricating structure 1 further includes a second axial oil groove 15, an inlet end of the second axial oil groove 15 is communicated with the axial oil groove 11 through a discharge groove 16, and an outlet end is communicated with the avoiding hole 6.

Specifically, the second axial oil groove 15 interfaces with the relief hole 6 and communicates with the drain groove 16. The second axial oil groove 15 introduces the lubricating oil in the discharge groove 16 to provide sufficient lubrication and cooling for the contact area of the tail part of the sliding vane 3 and the sliding chute 4; since this region is the key support point for preventing the vane 3 from deflecting, the provision of the second axial oil groove 15 can reduce significant frictional power consumption and prevent wear of the trailing portion of the vane 3.

In a specific embodiment:

as shown in fig. 6, the axial oil grooves 11 and/or the radial passages 12 are inclined such that the included angle therebetween is an obtuse angle.

Specifically, the axial oil groove 11 and/or the radial channel 12 are obliquely arranged, and the central included angle between the axial oil groove 11 and the radial channel 12 is larger than 90 degrees; along the flowing direction of the lubricating oil, the distance from the axial oil groove 11 to the center of the crankshaft 2 is gradually increased, the inclined axial oil groove 11 can enable viscous power generated by the reciprocating motion of the sliding sheet 3 to generate axial components, bubble-shaped gaseous refrigerant in the lubricating oil can be accelerated to be discharged out of the lubricating structure 1, and the leakage of a sliding sheet gap is reduced; the inclined radial channel 12 eliminates a plug structure, and can reduce the processing and assembling cost.

When the lubrication structure 1 is applied to a parallel-bar compressor, as shown in fig. 9, the cylinder assembly 5 includes two cylinders, and when the two cylinders are an upper cylinder 51 and a lower cylinder 52, respectively, the cylinder assembly 5 further includes a middle partition plate 53 disposed between the upper cylinder 51 and the lower cylinder 52, and the axial oil groove 11 is formed on a wall of a sliding groove of the upper cylinder 51; the cylinder assembly 5 further includes a second upper bearing 54 provided at an upper end surface of the upper cylinder 51 and a second lower bearing 55 provided at a lower end surface of the lower cylinder 52.

The lubricating structure 1 further comprises a third axial oil groove 101 formed in the sliding groove wall of the lower cylinder 52 and a second radial channel 102 formed in the middle partition plate 53, one end of the second radial channel 102 is communicated with the inner cavity of the middle partition plate 53, a second plug 103 is arranged at the other end of the second radial channel 102, one end of the axial oil groove 11 is communicated with the second radial channel 102, the other end of the axial oil groove is communicated with the upper discharge groove 104, one end of the third axial oil groove 101 is communicated with the second radial channel 102, and the other end of the third axial oil groove is communicated with the lower discharge groove 105.

In this embodiment, the second radial passage 102 is disposed on the middle partition plate 53, so as to avoid the reliability problems of the conventional lubrication structure disposed on the bearing, such as the weakening of the bearing structure, the large deformation of the bearing, and the like.

Wherein, the upper discharge groove 104 is arranged on the upper end surface of the upper cylinder 51, and the lower discharge groove 105 is arranged on the lower end surface of the lower cylinder 52; alternatively, the upper discharge groove 104 is formed in the lower end surface of the second upper bearing 54, and the lower discharge groove 105 is formed in the upper end surface of the second lower bearing 55.

Specifically, the oil supply hole 21 is located on the intermediate shaft between the two eccentric portions of the crankshaft 2, the inner cavity of the intermediate partition 53 serves as the ring groove 13, and the second radial passage 102 provided on the intermediate partition 53 simultaneously supplies the axial oil groove 11 of the upper cylinder 51 and the third axial oil groove 101 of the lower cylinder 52 with lubricating oil. The lubricating device has the advantages that the lubricating of the double-cylinder sliding vane is realized by only one set of oil supply flow path, the structure is simple and reliable, and the cost is low; because during the actual operation of the double-cylinder compressor, the oil level of the compressor is lower, the lubrication and sealing problems of the sliding sheet are more serious than those of a single cylinder, and the structure has a better and remarkable performance improving effect.

As shown in fig. 10, the axial oil groove 11 penetrates the groove wall of the upper cylinder 51, the middle diaphragm 53, and the groove wall of the lower cylinder 52.

Specifically, the oil supply hole 21 is disposed on the short shaft of the crankshaft 2, the ring groove 13 and the radial channel 12 are disposed in the second lower bearing 55, the axial oil groove in the chute of the upper cylinder 51 and the axial oil groove in the chute of the lower cylinder 52 are connected in series through the circumferential oil groove on the middle partition plate 53, that is, the axial oil groove 11 sequentially penetrates through the chute wall of the upper cylinder 51, the middle partition plate 53 and the chute wall of the lower cylinder 52, and this structure can also satisfy the lubrication of the twin-cylinder chute, and only one set of discharge grooves needs to be disposed on the lower surface of the second upper bearing 54 or the upper surface of the lower cylinder 52.

Example 2

The present embodiment provides a compressor including the pump body structure in embodiment 1.

The compressor that this embodiment provided can be so that clearance and bearing oil groove between gleitbretter and the spout all obtain sufficient lubricating oil flow to in the pipeline in lubricating oil arrival clearance, lubricating oil can reach certain axial flow speed, and then takes away the bubbly gaseous state refrigerant that the frictional heating produced fast, avoids the gleitbretter clearance leakage increase problem that gaseous state refrigerant gathering leads to.

Example 3

The present embodiment provides an air conditioner including the compressor of embodiment 2.

In summary, it is easily understood by those skilled in the art that the advantageous technical features described above can be freely combined and superimposed without conflict.

While the utility model has been described with reference to the preferred embodiments, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the utility model as defined by the appended claims.

Claims

1. A pump body structure is characterized in that the pump body structure is used for a compressor and comprises a lubricating structure (1), wherein the inlet end of the lubricating structure (1) is communicated with an oil supply hole (21) on a crankshaft (2) of the compressor, and the outlet end of the lubricating structure is communicated with a gap between a sliding vane (3) and a sliding groove (4) of the compressor;

the pump body structure further comprises a cylinder assembly (5), the lubricating structure (1) comprises an axial oil groove (11) formed in the wall of the sliding groove of the cylinder assembly (5), and the flow sectional area of the axial oil groove (11) is smaller than that of the oil supply hole (21).

2. Pump body structure according to claim 1, characterized in that the flow cross-section of the axial oil groove (11) is greater than the flow cross-section of the gap.

3. The pump body structure according to claim 1 or 2, characterized in that a flow cross-sectional area between the axial oil groove (11) and the oil supply hole (21) satisfies: S/S1 is less than 0.8; s is the cross-sectional flow area of the axial oil groove (11), and S1 is the cross-sectional flow area of the oil supply hole (21).

4. The pump body structure according to claim 2, characterized in that the flow cross-sectional area of the axial oil groove (11) and the flow cross-sectional area of the gap satisfy: S/S2 is more than 1.5; s is the flow cross-sectional area of the axial oil groove (11), and S2 is the flow cross-sectional area of the gap.

5. Pump body structure according to claim 4, characterized in that the axial oil groove (11) divides the sealing surfaces of the slide (3) and the runner (4) into a first sealing surface and a second sealing surface, the first sealing surface and the second sealing surface having a width such as to satisfy: 0.4 < (L1+ L2)/L < 1; wherein, L1 is the width of the first sealing surface, L2 is the width of the second sealing surface, and L is the distance between the avoidance hole (6) of the compressor and the inner wall of the cylinder assembly (5).

6. The pump body structure according to claim 5, wherein the first and second sealing surfaces have widths that satisfy: 0.6 < (L1+ L2)/L < 0.9.

7. Pump body structure according to claim 1 or 2, characterized in that the chute wall is connected with the axial oil groove (11) by a transition section (111), which is a curve, the tangent of which at the end point makes an obtuse angle with the chute wall.

8. The pump body structure according to claim 1 or 2, characterized in that the cylinder assembly (5) comprises at least one cylinder.

9. The pump body structure according to claim 8, wherein, when the cylinder assembly (5) comprises a cylinder, the lubricating structure (1) further comprises a radial channel (12) which opens in the lower bearing (7) of the pump body structure and communicates with the axial oil groove (11), one end of the radial channel (12) communicating with the oil supply hole (21) through the annular groove (13) and the other end being provided with a plug (14).

10. A pump body structure according to claim 9, characterized in that the lubricating structure (1) further comprises a second axial oil sump (15), the inlet end of the second axial oil sump (15) communicating with the axial oil sump (11) through a discharge groove (16), the outlet end communicating with the relief hole (6).

11. Pump body structure according to claim 9 or 10, characterized in that the axial oil grooves (11) and/or the radial channels (12) are arranged obliquely so that the angle between them is obtuse.

12. The pump body structure according to claim 8, wherein, when the cylinder assembly (5) comprises two cylinders, an upper cylinder (51) and a lower cylinder (52), respectively, the cylinder assembly (5) further comprises a middle partition plate (53) disposed between the upper cylinder (51) and the lower cylinder (52), the axial oil groove (11) being formed in a wall of a sliding groove of the upper cylinder (51); the cylinder assembly (5) further comprises a second upper bearing (54) arranged on the upper end surface of the upper cylinder (51) and a second lower bearing (55) arranged on the lower end surface of the lower cylinder (52).

13. A pump body structure according to claim 12, characterized in that the lubricating structure (1) further comprises a third axial oil groove (101) provided in the wall of the sliding groove of the lower cylinder (52) and a second radial channel (102) provided in the intermediate partition (53), one end of the second radial channel (102) being in communication with the inner cavity of the intermediate partition (53) and the other end being provided with a second stopper (103), one end of the axial oil groove (11) being in communication with the second radial channel (102) and the other end being in communication with the upper discharge groove (104), one end of the third axial oil groove (101) being in communication with the second radial channel (102) and the other end being in communication with the lower discharge groove (105).

14. The pump body structure according to claim 13, characterized in that the upper discharge groove (104) is opened in an upper end face of the upper cylinder (51), and the lower discharge groove (105) is opened in a lower end face of the lower cylinder (52).

15. The pump body structure according to claim 13, characterized in that the upper discharge groove (104) opens at a lower end face of the second upper bearing (54), and the lower discharge groove (105) opens at an upper end face of the second lower bearing (55).

16. The pump body structure according to claim 12, wherein the axial oil groove (11) penetrates through a groove wall of the upper cylinder (51), the center diaphragm (53), and a groove wall of the lower cylinder (52).

17. A compressor, characterized in that it comprises a pump body structure according to any one of claims 1 to 16.

18. An air conditioner characterized in that it comprises a compressor according to claim 17.