CN117287390A - Oscillating rotor type compressor - Google Patents

Abstract

The invention provides a pump body assembly and a swing rotor type compressor. The invention provides a pump body component, which comprises a crankshaft structure, a piston, a sliding vane, a cylinder, a main bearing and an auxiliary bearing, wherein the crankshaft structure comprises a pump oil hole and an eccentric oil outlet which are mutually communicated, the piston is provided with a hinged mounting groove and a piston oil outlet, the eccentric oil outlet is communicated with the piston oil outlet, the piston oil outlet is communicated with the hinged mounting groove, the cylinder is provided with the sliding vane mounting groove, one end of the sliding vane is arranged in the sliding vane mounting groove, the other end of the sliding vane is hinged and matched with the hinged mounting groove, the part of the sliding vane hinged in the hinged mounting groove is provided with an oil guide groove, the oil guide groove is communicated with the piston oil outlet, and the oil guide groove can be communicated with a cavity between the cylinder and the piston in the working process of the pump body component. The pump body assembly has good sealing performance, can reduce the internal leakage of the compression cavity and improve the energy efficiency of the compressor.

Description

Oscillating rotor type compressor

Technical Field

The invention relates to the technical field of compressors, in particular to a swing rotor type compressor.

Background

Rotary compressors are widely used in the temperature conditioning industry, such as air conditioning, refrigerators, heat pumps, etc., with their excellent combination of properties in the current refrigeration industry. The rotary compressor in the prior art mainly includes a wobble rotor type compressor and a rolling rotor type compressor.

Rolling rotor compressors have the advantage of low cost, but their sliding vane cannot be fully and reliably contact sealed with the outer diameter of the rolling rotor (piston), resulting in increased leakage in the compressor. And under the condition of the same outer diameter size, the spring is used as the initial starting pressure, the spring structure occupies the radial size, so that the radial size of the compressor is increased, meanwhile, the structure of the cylinder is complex, the contact surface between the sliding vane groove of the cylinder and the sliding vane is greatly reduced due to the spring hole, and the sliding vane groove is more easily worn.

The swing rotor type compressor comprises a piston and sliding vane integrated structure and a fixed sliding vane structure. The integral structure of the piston sliding vane has large processing and production difficulty, low economic benefit of finished products and large process complexity due to the difference of square and round structures of the sliding vane, so the integral structure cannot be widely applied to production. The fixed sliding vane type structure mainly adopts a sliding vane and rotor hinging mode, but the oil way of the existing swing rotor type compressor is only capable of achieving the lubricating effect between the sliding vane and the air cylinder, and the sealing performance is poorer than that of a piston sliding vane integrated structure, and is difficult to be improved. For example, patent publication CN2399533Y discloses a wobble rotor type compressor which can achieve a lubrication effect between a slide and a cylinder, but the lubrication effect is still insufficient and there is no improvement in sealing performance. At present, the piston sliding vane non-integrated swing rotor type compressor still has the problems that the lubrication effect of other parts is insufficient and the sealing performance is difficult to improve.

Disclosure of Invention

Based on this, it is necessary to provide a swing rotor type compressor having a good lubrication effect and a good sealing property.

The invention provides a swing rotor type compressor, which comprises a shell and a swing rotor type compressor pump body, wherein the swing rotor type compressor pump body is positioned in the shell, the swing rotor type compressor pump body comprises a crankshaft structure, a piston, a sliding vane, an air cylinder, a main bearing and an auxiliary bearing, the crankshaft structure, the piston and the air cylinder are sequentially arranged from inside to outside, the crankshaft structure penetrates through the air cylinder, the main bearing and the auxiliary bearing, the sliding vane and the air cylinder are positioned between the main bearing and the auxiliary bearing, a sliding vane mounting groove is formed in the air cylinder, one end of the sliding vane is mounted in the sliding vane mounting groove, the other end of the sliding vane is in hinged fit with the hinged mounting groove, the crankshaft structure comprises an oil pumping hole and an eccentric oil outlet which are mutually communicated, the piston is provided with the hinged mounting groove and the piston oil outlet, the part of the sliding vane hinged in the hinged mounting groove is provided with an oil guide groove, the oil guide groove is communicated with the piston oil outlet, and the sliding vane can be communicated with the piston oil guide groove in the air cylinder during the operation of the swing rotor type compressor, and the sliding vane can be moved between the sliding vane and the piston in the oil guide groove and the air cylinder.

Preferably, the end part of the sliding sheet hinged in the hinge mounting groove of the piston is provided with a clearance, the clearance is provided with a clearance with the bottom wall of the hinge mounting groove, an oil storage channel can be formed between the clearance and the hinge mounting groove, the piston oil outlet is communicated with the oil storage channel, and the oil guide groove is communicated with the oil storage channel.

Preferably, the sliding vane divides the compression chamber of the swing rotor compressor into a low pressure chamber side and a high pressure chamber side, and the oil guiding groove is positioned at one side of the sliding vane close to the low pressure chamber.

Preferably, the sliding vane comprises a sliding vane main body part, one side of the sliding vane main body is connected with a sliding vane hinging cylindrical part protruding relative to the sliding vane main body, and the tail end of the sliding vane hinging cylindrical part far away from the sliding vane main body is cut off to form a clearance space.

Preferably, the hinged installation groove is in a major arc shape, the diameter of the hinged cylindrical part of the sliding sheet is larger than the width of the opening of the hinged installation groove, the oil guiding groove is positioned on the hinged cylindrical part of the sliding sheet, and the opening of the oil guiding groove is connected with the avoidance space.

Preferably, the oil guiding groove is arranged between the upper end face and the lower end face of the sliding sheet hinged cylindrical part.

Preferably, the upper end face and the lower end face of the sliding vane are both provided with a longitudinal oil guiding groove and a transverse oil guiding groove, and the longitudinal oil guiding groove extends from the sliding vane main body to the tail end of the sliding vane hinged cylindrical part and is connected with the avoidance space; the transverse oil guiding groove is positioned on the sliding vane main body and transversely penetrates through the longitudinal oil guiding groove.

Preferably, a first lubricating oil channel is formed between the longitudinal oil guiding groove and the transverse oil guiding groove on the upper end face of the sliding vane and the main bearing, a second lubricating oil channel is formed between the longitudinal oil guiding groove and the transverse oil guiding groove on the lower end face of the sliding vane and the auxiliary bearing, and the first lubricating oil channel and the second lubricating oil channel are communicated with the oil storage channel.

Preferably, the crankshaft structure comprises a shaft main body and an eccentric shaft, the eccentric shaft is sleeved outside the shaft main body, the shaft main body penetrates through the eccentric shaft, a pump oil hole and a main body oil outlet are formed in the shaft main body, the pump oil hole is communicated with the main body oil outlet, the eccentric shaft is provided with an eccentric oil outlet which penetrates through the eccentric shaft wall in the radial direction, the eccentric oil outlet is communicated with the pump oil hole, a transverse oil groove and a longitudinal oil groove are formed in the outer wall of the eccentric shaft, the transverse oil groove and the longitudinal oil groove are communicated with the eccentric oil outlet, the longitudinal oil groove extends along the axial direction of the eccentric shaft, a side wall is formed at one end of the longitudinal oil groove, a side opening is formed at the other end of the longitudinal oil groove, and the piston oil outlet is communicated with the transverse oil groove.

Preferably, the piston comprises a piston main body, a first sealing strip and a second sealing strip, wherein a first auxiliary sealing groove and a second auxiliary sealing groove are respectively arranged on the upper end face and the lower end face of the piston, steps are respectively arranged in the first auxiliary sealing groove and the second auxiliary sealing groove, the first sealing strip is arranged on the steps of the first auxiliary sealing groove, and a first gas channel is arranged between the first sealing strip and the bottom wall of the first auxiliary sealing groove; a second gas channel is arranged between the first sealing strip and the bottom wall of the first auxiliary sealing groove; the piston main body is provided with a first gas connecting hole and a second gas connecting hole, one end of the first gas connecting hole is communicated with the first gas channel, and the other end of the first gas connecting hole is communicated with the outer cylindrical surface of the piston main body; one end of the second gas through hole is communicated with the second gas channel, and the other end of the second gas through hole is communicated with the outer cylindrical surface of the piston main body.

The invention relates to a piston sliding vane non-integral type swing rotor type compressor, which is characterized in that an oil guide groove is arranged at the part of a sliding vane hinged in a hinged mounting groove, so that lubricating oil can enter a cavity between a cylinder and a piston along with the movement of a crankshaft structure in the working process of a pump body assembly, on one hand, lubrication is provided between the cylinder and the piston, on the other hand, the tightness of the matching surfaces of the cylinder and the piston can be enhanced, the internal leakage of a compression cavity is reduced, and the energy efficiency of the compressor is improved.

Drawings

The foregoing and other objects, features and advantages of the invention will be apparent from the following more particular description of preferred embodiments of the invention, as illustrated in the accompanying drawings. Like reference numerals refer to like parts throughout the drawings, and the drawings are not intentionally drawn to scale on actual size or the like, with emphasis on illustrating the principles of the invention.

Fig. 1 is a schematic diagram of a pump assembly according to the present invention.

Fig. 2 is an enlarged schematic view of the part "a" in fig. 1.

Fig. 3 is a schematic structural diagram of a crankshaft structure provided by the present invention.

Fig. 4 is a schematic diagram of the structure of the eccentric shaft provided by the invention.

Fig. 5 is a schematic view of a sliding vane structure according to the present invention.

Fig. 6 is a schematic diagram of a matching structure of a sliding vane and a piston provided by the invention.

Fig. 7 is an enlarged schematic view of the part "B" of fig. 6.

Fig. 8 is a schematic diagram of a piston structure according to a first embodiment of the present invention.

Fig. 9 is a schematic diagram of a cylinder structure provided by the invention.

Fig. 10 is a schematic structural view of the pump assembly provided by the present invention in a first motion state.

Fig. 11 is a schematic structural view of the pump body assembly provided by the invention in the second motion state.

Fig. 12 is a schematic structural view of the pump assembly provided by the present invention in a third movement state.

Fig. 13 is a schematic diagram of a piston structure according to a second embodiment of the present invention.

Fig. 14 is a schematic diagram of a piston main body according to a second embodiment of the present invention.

Fig. 15 is an enlarged schematic view of the part "C" of fig. 14.

Fig. 16 is a schematic diagram of a piston-cylinder matching structure according to a second embodiment of the present invention.

Detailed Description

In order that the invention may be understood more fully, the invention will be described with reference to the accompanying drawings.

It will be understood that when an element is referred to as being "connected" to another element, it can be directly connected to and integrated with the other element or intervening elements may also be present. The terms "mounted," "one end," "the other end," and the like are used herein for illustrative purposes only.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art. The terminology used in the description herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and/or" as used herein includes any and all combinations of one or more of the associated listed items.

Referring to fig. 1, the invention provides a pump body assembly comprising a crankshaft structure 1, a sliding vane 2, a piston 3, a cylinder 4, a main bearing 5 and a secondary bearing 6, wherein the crankshaft structure 1 penetrates through the cylinder 4, the main bearing 5 and the secondary bearing 6, and the sliding vane 2 and the cylinder 4 are positioned between the main bearing 5 and the secondary bearing 6. The crankshaft structure 1, the piston 3 and the cylinder 4 are sequentially arranged from inside to outside.

Referring to fig. 1 and 3, the crankshaft structure 1 includes a shaft main body 11 and an eccentric shaft 12.

Referring to fig. 1 and 3, the shaft body 11 includes a main shaft 111 and a sub shaft 112 connected to each other, a pump oil hole 1121 and a sub shaft oil outlet 1122 are provided on the sub shaft 112, a main shaft oil outlet 1111 is provided on the main shaft 111, a main shaft oil outlet includes a main shaft oil outlet 1111 and a sub shaft oil outlet 1122, a pump oil passage 113 is provided in the shaft body 11, and the pump oil passage 113 communicates with the pump oil hole 1121 and the main shaft oil outlet 1122. The lubricating oil is fed from the pump oil hole 1121, then enters the pump oil passage 113, and finally is discharged out of the shaft body 11 through the body oil outlet hole and the eccentric oil outlet hole 121.

Referring to fig. 1 and 3, the eccentric shaft 12 is sleeved outside the shaft body 11, and the shaft body 11 penetrates the eccentric shaft 12. The eccentric shaft 12 includes an eccentric oil outlet hole 121, a transverse oil groove 122 and a longitudinal oil groove 123, and the eccentric oil outlet hole 121 penetrates through the wall of the eccentric shaft 12 in the radial direction. The transverse oil groove 122 and the longitudinal oil groove 123 are formed in the outer wall of the eccentric shaft 12 and are communicated with the eccentric oil outlet hole 121.

Referring to fig. 3-4, the eccentric shaft 12 is provided with a thrust surface clearance step 124 and a thrust surface 125, and the thrust surface 125 is a mating surface with a bearing, and plays a supporting role on the premise of meeting the sealing. The side opening of the longitudinal oil groove 123 communicates with the thrust surface relief step 124.

Referring to fig. 3 to 4 and 10, one end of the lateral oil groove 122 in the extending direction thereof has a sidewall, and the other end is connected to the longitudinal oil groove 123 and the eccentric oil outlet hole 121. The lateral oil groove 122 is bordered by the piston oil outlet to form a passage, and the total oil intake is controlled by the magnitude of the radian. The angle f of the transverse oil groove 122 described with reference to fig. 10 is less than 90 degrees, and may be, for example, 10-90 degrees. The angle of the transverse oil groove 122 in this embodiment may be the angle formed between the side wall at one end of the transverse oil groove 122 and the opening at the other end, or may be as shown in fig. 10: an angle is formed between one end side wall of the transverse oil groove 122 and the side wall of the eccentric oil outlet hole 121. The smaller the angle, the shorter the total on-time, the smaller the amount of oil introduced, and vice versa.

Referring to fig. 3-4, a longitudinal oil groove 123 extends axially along the eccentric shaft 12. The longitudinal oil groove 123 has a side wall 123a at one end and a side opening 123b at the other end. The lubricating oil in the crankshaft structure 1 flows to the eccentric oil outlet hole 121, and enters the transverse oil groove 122 and the longitudinal oil groove 123 through the eccentric oil outlet hole 121.

Referring to fig. 3-4, one end of the longitudinal oil groove 123 has a side wall 123a to form a temporary small oil storage groove after being matched with the piston 3, so that lubricating oil can be provided for the inner surface of the piston 3, and meanwhile, the side opening 123b of the longitudinal oil groove 123 is communicated with the thrust surface clearance step 124, so that the temporary small oil storage groove can guide oil upwards to the thrust surface 125 of the eccentric shaft 12, and a better lubricating effect is achieved. The transverse oil groove 122 and the inner diameter of the piston 3 form a passage, and the total oil inlet amount is controlled through the radian, so that a good lubricating effect is ensured.

Referring to fig. 2 and 4, the lateral oil groove 122 of the crankshaft structure 1 is connected with the piston 3 inner diameter side outlet piston oil outlet hole 31 to form a passage, and the total oil intake amount is controlled by the magnitude of the radian. One end of the longitudinal oil groove 123 of the crankshaft structure 1 is provided with a side wall, so that a temporary small oil storage groove is formed after the eccentric shaft 12 of the crankshaft structure is matched with the piston 3, lubricating oil can be provided for the inner surface of the piston 3, and meanwhile, the lubricating oil can be upwards guided to a thrust surface of the eccentric shaft 12.

Referring to fig. 3 to 4, the eccentric oil outlet hole 121 is located between the side wall 123a and the side opening 123b of the longitudinal oil groove 123, which is located at the intersection of the lateral oil groove 122 and the longitudinal oil groove 123.

Referring to fig. 5 to 7, the sliding vane 2 includes a main body 21 of the sliding vane 2, and a sliding vane hinge cylindrical portion 22 protruding with respect to the main body of the sliding vane 2 is connected to one side of the main body of the sliding vane 2, and the maximum radius of the sliding vane hinge cylindrical portion 22 is greater than the width of the main body of the sliding vane 2, however, in some thicker sliding vane embodiments, the maximum radius of the hinge cylindrical portion 22 may be consistent with the width of the main body of the sliding vane. The end of the slider hinged cylindrical portion 22 remote from the body of the slider 2 is cut to form the clearance space 221, and the cutting is not limited to the cutting and is formed by cutting the end portion of the cylindrical portion. Referring to fig. 7, the avoidance space 221 and the piston 3 form an oil storage channel 33, and the oil storage channel 33 forms a small oil storage space, which can accommodate a certain amount of lubricating oil, so as to ensure that the hinge can slide sufficiently when the compressor rotates at a high speed, and avoid the occurrence of dry grinding and blocking.

Referring to fig. 5 to 7, the slide hinge cylindrical portion 22 is provided with an oil guide groove 222, an opening of the oil guide groove 222 is connected with the avoidance space 221, and the avoidance space 221 and the piston 3 form an oil storage channel 33. The lubricating oil is introduced into the oil storage channel 33 between the avoidance space 221 and the piston 3, so that a better lubricating effect is provided between the sliding vane 2 and the piston 3, and the abrasion between the sliding vane 2 and the piston 3 is reduced. Meanwhile, as the avoidance holes 221 are formed, the highest point on the cylindrical surface disappears, and the tangent lines between the sliding vane 2 and the piston 3 are changed into two, so that two sealing positions are formed, and the sealing enhancing effect is achieved. Realizing better sealing effect.

Referring to fig. 5, the oil guide groove 222 is located at one side of the slider hinge cylindrical portion 22 and between the upper end surface 212 and the lower end surface 211. The upper end face 212 and the lower end face 211 referred to in the present embodiment are referred to in the up-down direction referred to in fig. 5, and the up-down direction is opposite. The sliding vane 2 divides the compressor into a low pressure cavity side and a high pressure cavity side, and the side close to the low pressure cavity is the low pressure side of the sliding vane 2. The oil guide groove 222 is positioned on the low pressure side of the sliding vane 2, so that the oil guide groove not only maintains enough lubricating oil to lubricate the outer diameter of the piston 3 and the inner diameter of the cylinder 4, but also enhances the tightness of one side of the suction low pressure cavity by utilizing an oil film.

Referring to fig. 5, the upper end surface 212 and the lower end surface 211 of the sliding vane 2 are both provided with a longitudinal oil guiding groove 222 and a transverse oil guiding groove 214, the longitudinal oil guiding groove 213 extends from the sliding vane 2 main body to the end of the sliding vane hinge cylindrical portion 22 and is connected with the avoidance space 221, and the transverse oil guiding groove 314 is located on the sliding vane 2 main body and transversely penetrates through the longitudinal oil guiding groove 213, so that an oil film seal is formed.

Returning to fig. 2, a first lubricating oil channel 51 is formed between the longitudinal oil guiding groove 213 and the transverse oil guiding groove 214 of the upper end face 212 of the sliding vane 2 and the main bearing 5, a second lubricating oil channel 61 is formed between the longitudinal oil guiding groove 213 and the transverse oil guiding groove 214 of the lower end face 211 of the sliding vane 2 and the auxiliary bearing 6, and the first lubricating oil channel 51 and the second lubricating oil channel 52 are both communicated with the oil storage channel 33.

Referring to fig. 5, the body 21 of the sliding vane 2 is away from the side of the sliding vane hinged cylindrical portion 22, which is a continuous plane, the sliding vane 2 does not need to be provided with a spring mounting groove, the tail of the sliding vane can be a flat plane, the sliding vane 2 is simplified, the processing difficulty is reduced, and the cost is reduced.

Referring to fig. 6-8 and 13-16, the piston 3 includes a piston body 300, a first seal 301, and a second seal 302.

Referring to fig. 6 to 8, the piston 3 is provided with a hinge mounting groove 32 and a piston oil outlet hole 31, the hinge mounting groove 32 penetrates through an upper end surface 33 and a lower end surface of the piston 3 in the axial direction, and the piston oil outlet hole 31 penetrates through the piston 3 in the radial direction and communicates with the hinge mounting groove 32. A specific piston oil outlet hole 31 is opened in the bottom wall of the hinge mounting groove 32.

Referring to fig. 13 to 16, the upper end surface 33 and the lower end surface of the piston main body 300 are respectively provided with a first auxiliary sealing groove 351 and a second auxiliary sealing groove 352, steps 3511 are respectively arranged in the first auxiliary sealing groove 351 and the second auxiliary sealing groove 352, a first sealing strip 301 is arranged above the steps 3511 of the first auxiliary sealing groove 351, and a first gas channel is arranged between the first sealing strip 301 and the bottom wall 3512 of the first auxiliary sealing groove 351; a second gas passage is formed between the second seal strip 302 and the bottom wall of the first auxiliary seal groove 352; the piston main body 300 is provided with a first gas connecting hole 361 and a second gas connecting hole 362, one end of the first gas connecting hole 361 is communicated with the first gas channel, and the other end is communicated with the compression cavity 37 between the piston main body and the cylinder; the second gas passage 362 has one end communicating with the second gas passage and the other end communicating with the compression chamber 37 of the piston body.

In this embodiment, a first auxiliary sealing groove 351 and a second auxiliary sealing groove 352 are provided, the groove can be designed into a complete ring shape or an arc shape according to actual needs, and small steps (such as step 3511) are arranged in the groove, and auxiliary sealing strips (the first sealing strip 301 and the second sealing strip 302) are arranged on the steps. The sealing strip is arranged in the sealing groove and used for enhancing the sealing performance of the compression cavity, the square-section sealing strip is the easiest to obtain the appearance structure, and the sealing strip can be designed into semicircular, round, T-shaped and other section forms.

The gas channel formed under the step is used for introducing high-pressure gas, and is outwards supported under the auxiliary sealing of an oil film to be respectively and tightly attached to the end surfaces of the corresponding upper bearing and the lower bearing so as to enhance the sealing performance of the compression cavity, reduce the leakage of the compression cavity to the minimum and integrally improve the energy efficiency of the compressor.

Returning to fig. 2, the eccentric oil outlet 121 of the crankshaft structure 1 is disposed opposite to and communicates with the piston oil outlet 31. The piston oil outlet hole 31 is also provided opposite to and in communication with the oil guide groove 222 of the vane 2 for guiding the lubricating oil into the oil guide groove 222 of the vane 2. The lubricating oil enters the longitudinal oil groove 123 through the eccentric oil outlet hole 121, and can be guided upward to the thrust surface of the eccentric shaft 12. The lubricating oil passing through the eccentric oil outlet hole 121 enters the oil guide groove 222 and the oil reservoir passage 33 through the piston oil outlet hole 31. The lubrication oil of the oil guide groove 222 and the oil reservoir passage 33 flows to the first lubrication oil passage 51 and the second lubrication oil passage 61.

Referring to fig. 6 to 8, the hinge mounting groove 32 is in a major arc shape, the diameter of the slider hinge cylindrical part 22 is larger than the opening width of the hinge mounting groove 32, the slider hinge cylindrical part 22 is in hinge fit with the hinge mounting groove 32, and the hinge mounting groove 32 is smaller in opening width to limit the slider hinge cylindrical part 22 to be hinged in the hinge mounting groove 32.

Referring to fig. 6 to 7, a gap is formed between the avoidance space 221 of the sliding vane 2 and the bottom wall of the hinge mounting groove 32, an oil storage passage 33 may be formed, and the oil guide groove 222 of the sliding vane 2 communicates 33 with the oil storage passage.

Referring to fig. 9, a vane mounting groove 41 is provided on the cylinder 4, one end of the body portion 21 of the vane 2, which is remote from the vane hinge cylindrical portion 22, is mounted in the vane mounting groove 41, and the vane moves relative to the vane mounting groove 41. In this embodiment, because the sliding vane does not need to install the sliding vane spring, the sliding vane size is smaller, and the sliding vane spring does not need to be installed, the slotting of the air cylinder is shorter, the structure is simple, and the processing and the assembly are easier. And the outer diameter of the cylinder is obviously smaller than that of the cylinder under the traditional sliding vane structure, and the smaller volume saves the material cost under the same function.

Referring to fig. 10-12, the crankshaft structure 1 moves to oscillate the piston 3 around the inner diameter of the cylinder 4, referring to the compressor rotation direction g in fig. 10. The sliding vane 2 is always hinged and fixed to the piston 3 during the swinging of the piston 3, and can move up and down relative to the sliding vane mounting groove 41 along with the swinging of the piston 3 (the term "up and down" in this embodiment refers to fig. 10-12). The oil pumped by the crankshaft structure 1 enters the oil pumping channel 113 and then enters the transverse oil groove 122 through the eccentric oil outlet 121, so that lubrication between the crankshaft structure 1 and the piston 3 can be fully performed in the movement process of the crankshaft structure 1, and abrasion is avoided. The oil guide grooves 222 of the slide are provided so that lubricating oil can enter between the piston 3 and the cylinder 4 (refer to fig. 12), providing sufficient lubrication and enhanced sealing for the outer diameter of the piston 3 and the inner diameter of the cylinder 4.

The pump body component provided by the invention provides a brand new oil way structure, which can fully lubricate the connecting and matching positions of all parts in the pump body component, and meanwhile, the arrangement of the oil guide groove ensures that the lubricating oil entering the air suction low-pressure cavity can enhance the tightness of the matching surfaces of the piston and the air cylinder while lubricating the inner diameters of the piston and the air cylinder, thereby reducing the internal leakage of the compressor and improving the energy efficiency of the compressor.

The invention also provides a swing rotor type compressor which comprises a shell and the pump body assembly, wherein the pump body assembly is positioned in the shell, and a low-pressure air inlet and a high-pressure air outlet are formed in the shell.

In this application, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.

In the description of the present specification, a description referring to the terms "preferred embodiment," "further embodiment," "other embodiments," or "specific examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present application. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.

Although embodiments of the present application have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the application, and that variations, modifications, alternatives, and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the application.

Claims (10)

1. The utility model provides a swing rotor formula compressor, its characterized in that, includes the shell and swing rotor formula compressor pump body, the swing rotor formula compressor pump body is located in the shell, the swing rotor formula compressor pump body includes bent axle structure, piston, gleitbretter, cylinder, main bearing and auxiliary bearing, bent axle structure, piston and cylinder set gradually from interior to exterior, the bent axle structure runs through cylinder, main bearing and auxiliary bearing, gleitbretter and cylinder are located between main bearing and the auxiliary bearing, be provided with the gleitbretter mounting groove on the cylinder, gleitbretter one end install in the gleitbretter mounting groove, the gleitbretter other end with hinge mounting groove articulates the cooperation, the bent axle structure includes pump oilhole and the eccentric oil outlet of intercommunication each other, be provided with hinge mounting groove and piston oil outlet on the piston, the eccentric oil outlet intercommunication the piston oil outlet articulates the mounting groove, the gleitbretter articulates in the part in the hinge mounting groove and is provided with the oil guide groove, the oil guide groove with the piston oil outlet intercommunication, swing rotor formula compressor is in the work and the gleitbretter is in the oil guide groove and the cylinder is in the motion.

2. The wobble rotor type compressor as set forth in claim 1, wherein the end of the sliding vane hinged in the hinge mounting groove of the piston has a clearance gap with a bottom wall of the hinge mounting groove, an oil storage passage may be formed between the clearance gap and the hinge mounting groove, a piston oil outlet communicates with the oil storage passage, and the oil guide groove communicates with the oil storage passage.

3. The swing rotor type compressor according to claim 1, wherein the vane divides a compression chamber of the swing rotor type compressor into a low pressure chamber side and a high pressure chamber side, and the oil guide groove is located at a side of the vane adjacent to the low pressure chamber.

4. The swing rotor type compressor according to claim 1, wherein the vane comprises a vane body portion, one side of the vane body is connected with a vane hinge cylindrical portion protruding relative to the vane body, and an end of the vane hinge cylindrical portion away from the vane body is cut away to form a clearance space.

5. The swing rotor type compressor according to claim 1, wherein the hinge mounting groove is in a major arc shape, a diameter of the vane hinge cylindrical part is larger than an opening width of the hinge mounting groove, the oil guiding groove is positioned on the vane hinge cylindrical part, and an opening of the oil guiding groove is connected with the avoidance space.

6. The swing rotor type compressor according to claim 1, wherein the oil guide groove is provided between an upper end surface and a lower end surface of the vane hinge cylindrical portion.

7. The wobble rotor type compressor as claimed in claim 1, wherein the upper and lower end surfaces of the vane are provided with a longitudinal oil guiding groove and a transverse oil guiding groove, and the longitudinal oil guiding groove extends from the vane body to the end of the vane hinge cylindrical part and is connected with the avoidance space; the transverse oil guiding groove is positioned on the sliding vane main body and transversely penetrates through the longitudinal oil guiding groove.

8. The wobble rotor type compressor as set forth in claim 1, wherein a first lubricant passage is formed between the longitudinal and lateral lubricant grooves of the upper end surface of the vane and the main bearing, a second lubricant passage is formed between the longitudinal and lateral lubricant grooves of the lower end surface of the vane and the auxiliary bearing, and both the first lubricant passage and the second lubricant passage are communicated with the oil storage passage.

9. The wobble rotor compressor of claim 1, wherein the crankshaft structure includes a shaft main body and an eccentric shaft, the eccentric shaft is sleeved outside the shaft main body, the shaft main body penetrates through the eccentric shaft, a pump oil hole and a main body oil outlet are formed in the shaft main body, the pump oil hole is communicated with the main body oil outlet, the eccentric shaft is provided with the eccentric oil outlet penetrating through an eccentric shaft wall in the radial direction, the eccentric oil outlet is communicated with the pump oil hole, a transverse oil groove and a longitudinal oil groove are formed in the outer wall of the eccentric shaft, the transverse oil groove and the longitudinal oil groove are communicated with the eccentric oil outlet, the longitudinal oil groove extends along the axial direction of the eccentric shaft, one end of the longitudinal oil groove is provided with a side wall, the other end of the longitudinal oil groove is provided with a side opening, and the piston oil outlet is communicated with the transverse oil groove.

10. The wobble rotor compressor as claimed in claim 1, wherein the piston includes a piston main body, a first sealing strip and a second sealing strip, a first auxiliary sealing groove and a second auxiliary sealing groove are respectively provided at an upper end surface and a lower end surface of the piston, steps are provided in the first auxiliary sealing groove and the second auxiliary sealing groove, the first sealing strip is disposed on the steps of the first auxiliary sealing groove, and a first gas channel is provided between the first sealing strip and a bottom wall of the first auxiliary sealing groove; a second gas channel is arranged between the second sealing strip and the bottom wall of the second auxiliary sealing groove; the piston main body is provided with a first gas connecting hole and a second gas connecting hole, one end of the first gas connecting hole is communicated with the first gas channel, and the other end of the first gas connecting hole is communicated with a compression cavity between the piston main body and the cylinder; one end of the second gas through hole is communicated with the second gas channel, and the other end of the second gas through hole is communicated with the compression cavity between the piston main body and the cylinder.