CN216518497U - Piston assembly and compressor - Google Patents
Piston assembly and compressor Download PDFInfo
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- CN216518497U CN216518497U CN202122942297.1U CN202122942297U CN216518497U CN 216518497 U CN216518497 U CN 216518497U CN 202122942297 U CN202122942297 U CN 202122942297U CN 216518497 U CN216518497 U CN 216518497U
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Abstract
The utility model discloses a piston assembly and a compressor, wherein the piston assembly comprises a piston, a ball-and-socket joint and a sealing piece, the piston is provided with a piston head and a piston skirt, the piston skirt is of a hollow structure with two open ends, and the piston head is arranged at one open end of the piston skirt; the ball-and-socket joint is provided with a ball head and a retainer, the retainer is fixed in the piston skirt in a spot welding manner, the ball head is limited between the piston head and the retainer, a gap between two adjacent welding points is formed between the retainer and the piston skirt, and the ball head is used for being connected with the connecting rod; the sealing element can seal the gap when the piston works. The piston assembly can improve the efficiency of the compressor.
Description
Technical Field
The utility model relates to the technical field of compressors, in particular to a piston assembly and a compressor.
Background
In the compressor, a connecting rod is connected with a crankshaft and a piston in a piston assembly, and when a motor drives the crankshaft to rotate, the connecting rod drives the piston to reciprocate in a cylinder, so that the working processes of compression and exhaust are completed. In the related art, a piston assembly includes a piston and a ball joint. The piston is provided with a piston head and a piston skirt, the piston skirt is of a hollow structure with two open ends, and the piston head is arranged at one open end of the piston skirt. The ball joint comprises a ball seat, a ball head and a retainer. The ball seat is welded on the piston head. The retainer is welded on the ball seat and is matched with the ball seat to compress the ball head, so that the ball head is limited between the ball seat and the retainer. The ball head is connected with the connecting rod, so that the connection of the piston and the connecting rod is realized. However, due to the axial shrinkage deformation of the welding line between the ball seat and the piston head, the ball seat can generate extrusion force towards the retainer to the ball head, and due to the axial shrinkage deformation of the welding line between the retainer and the ball seat, the retainer can generate extrusion force towards the ball seat to the ball head, so that the ball head is excessively compressed. And the ball head is excessively compressed, so that the friction between the ball head and the retainer and the ball seat is increased, extra friction work is generated when the ball head moves, and the efficiency of the compressor is reduced. In order to reduce friction, the ball and socket joint needs to be pre-ground for hundreds of hours, so that the production efficiency is greatly reduced and the cost is increased.
SUMMERY OF THE UTILITY MODEL
The main object of the present invention is to propose a piston assembly aimed at increasing the efficiency of the compressor.
To achieve the above object, the present invention provides a piston assembly comprising:
the piston is provided with a piston head and a piston skirt, the piston skirt is of a hollow structure with two open ends, and the piston head is arranged at one open end of the piston skirt;
the ball-and-socket joint is provided with a ball head and a retainer, the retainer is fixed in the piston skirt in a spot welding manner, the ball head is limited between the piston head and the retainer, a gap between two adjacent welding points is formed between the retainer and the piston skirt, and the ball head is used for being connected with a connecting rod; and
a seal capable of sealing the void when the piston is in operation.
In one embodiment, the number of the welding points is multiple, and the welding points are arranged around the piston skirt at equal intervals.
In one embodiment, the retainer includes a holding portion for supporting the ball head, a welding portion for welding with the piston skirt, and a flat plate portion connecting the holding portion and the welding portion, and the holding portion and the welding portion are both located on a side of the flat plate portion away from the piston head.
In one embodiment, the retainer, the piston skirt and the piston head enclose a working space, the ball head is provided with an oil guide channel for supplying oil to the working space, and the oil guide channel extends along the arrangement direction of the retainer and the piston head.
In one embodiment, the oil guide channel comprises a connecting section and an oil guide section which are connected, the connecting section is used for a connecting rod to be inserted, and the inner diameter of the oil guide section is larger than that of the connecting section.
In one embodiment, the sealing element comprises an oil absorbing expansion sealing element arranged in the working space, the oil absorbing expansion sealing element is spaced from the retainer when the sealing element is not expanded, and after the sealing element is expanded, the oil absorbing expansion sealing element simultaneously interferes with the inner wall of the piston skirt and the retainer to seal the gap.
In an embodiment, the oil absorption expansion sealing element is a hollow structure with two open ends, the oil absorption expansion sealing element is sleeved outside the sphere, one end of the oil absorption expansion sealing element is connected with the piston head, the other end of the oil absorption expansion sealing element is adjacent to the retainer, the oil absorption expansion sealing element divides the working space into a first space located in the oil absorption expansion sealing element and a second space located between the oil absorption expansion sealing element and the piston skirt, the oil guiding hole is formed in the oil absorption expansion sealing element, the edge hole is formed in the piston skirt, and the oil guiding channel, the first space, the oil guiding hole, the second space and the edge hole are sequentially communicated.
In one embodiment, a positioning groove is defined between the inner wall of the piston skirt and the retainer, and an edge of one end of the oil expansion seal, which is away from the piston head, extends obliquely toward the inner wall of the piston skirt, and after expansion, the obliquely extending edge of the oil expansion seal is inserted into the positioning groove.
In one embodiment, the ball joint further comprises a ball seat, the ball seat is located in the working space and is arranged on the piston head, and an oil passage communicating the oil guide passage and the working space is formed between the ball seat and the ball head.
In an embodiment, the ball seat is provided with an oil guide area opposite to one end of the oil guide channel, the ball seat is provided with a plurality of oil guide grooves for forming the oil passing channel, and one ends of the plurality of oil guide grooves are converged in the oil guide area.
In one embodiment, the sealing member includes a sealant disposed at the void.
The present invention also proposes a compressor comprising:
the above-described piston assembly; and
and the connecting rod is connected with the ball head.
In the piston assembly, the retainer is fixed in the piston skirt in a spot welding manner, and the ball head is limited between the piston head and the retainer while the retainer is fixed in the piston skirt, so that axial contraction deformation of a welding point between the retainer and the piston skirt cannot cause the retainer to generate extrusion force towards the piston head on the ball head (because the force generated by the axial contraction deformation of the welding point and acting on the ball head is in the same direction as the force of the piston head acting on the ball head, the distance between the piston head and the retainer is basically unchanged, so that the axial contraction deformation of the welding point between the retainer and the piston skirt cannot cause the retainer to generate extrusion force towards the piston head on the ball head), so that excessive friction force cannot be generated between the ball head and the retainer and between the ball head and the piston head, extra friction work cannot be generated basically during the movement of the ball head, and the efficiency reduction of the compressor can be effectively avoided, the compressor can achieve better efficiency, and the piston assembly can improve the efficiency of the compressor.
Moreover, compared with a full circle of continuous annular welding lines, namely full welding, the force generated by axial shrinkage deformation of the welding points and the force generated by radial shrinkage deformation of the welding points are both small, the radial shrinkage deformation of the welding points basically cannot cause deformation of the piston skirt, the shape of the piston skirt basically cannot deviate from a cylindrical shape, and the radial shrinkage deformation of the welding points basically cannot cause poor cylindricity of the piston skirt. It should be noted that the shape of the skirt deviates from a cylindrical shape, i.e. the poorer the cylindricity of the skirt, the gas leakage may occur in the gap between the skirt and the cylinder, which leakage, during operation of the compressor, may reduce the efficiency of the compressor and lead to increased wear of the cylinder (including the piston). That is, the piston assembly described above can prevent the shape of the piston skirt from deviating from the cylindrical shape, thereby further improving the efficiency of the compressor and reducing the wear of the cylinder (including the piston).
In addition, the retainer is fixed in the piston skirt in a spot welding mode, so that the gap between two adjacent welding points has the risk of oil leakage, and the sealing element can seal the gap when the piston works, so that the problem of oil leakage can be solved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.
FIG. 1 is a schematic perspective view of a piston rod assembly according to an embodiment of the present invention;
FIG. 2 is an exploded perspective view of the piston rod assembly shown in FIG. 1;
FIG. 3 is a partial cross-sectional view of the piston rod assembly shown in FIG. 1;
fig. 4 is a perspective view illustrating a ball seat of the piston rod assembly shown in fig. 1.
The reference numbers illustrate:
| reference numerals | Name (R) | Reference numerals | Name (R) |
| 10 | Piston connecting rod device | 12 | Piston |
| 14 | Connecting |
200 | Piston |
| 300 | |
400 | |
| 210 | Piston |
220 | Piston |
| 310 | |
320 | |
| 322 | |
324 | Weld |
| 326 | |
312 | |
| 312a | Connecting |
312b | |
| 14a | |
12a | A |
| 12b | |
12c | Locating |
| 330 | |
12d | |
| 332 | |
330a | |
| 222 | Side hole |
The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that, if directional indications (such as up, down, left, right, front, and back … …) are involved in the embodiment of the present invention, the directional indications are only used to explain the relative positional relationship between the components, the movement situation, and the like in a specific posture (as shown in the drawing), and if the specific posture is changed, the directional indications are changed accordingly.
In addition, if there is a description of "first", "second", etc. in an embodiment of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, if appearing throughout the text, "and/or" is meant to include three juxtaposed aspects, taking "A and/or B" as an example, including either the A aspect, or the B aspect, or both A and B satisfied aspects. In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.
The utility model provides a piston connecting rod device.
In an embodiment of the present invention, as shown in fig. 1-3, the piston rod assembly 10 includes a piston assembly 12 and a connecting rod 14.
The piston assembly 12 includes a piston 200, a ball and socket joint 300, and a seal 400.
The piston 200 has a piston head 210 and a piston skirt 220. The piston skirt 220 is a hollow structure with two open ends, and the piston head 210 is disposed at one open end of the piston skirt 220. Specifically, in the present embodiment, the piston head 210 is located at the end of the piston skirt 220, and in this case, the piston 200 may be considered as a hollow structure having an open end and an end plate. More specifically, in the present embodiment, the piston head 210 and the piston skirt 220 are integrally formed.
In the present embodiment, a gap between two adjacent welding points is formed between the retainer 320 and the piston skirt 220. Seal 400 is capable of sealing the gap when piston 200 is in operation, and preventing lubricant from leaking out of the gap, that is, seal 400 is capable of sealing the gap when the compressor having piston assembly 12 is in operation, and preventing lubricant from leaking out of the gap, that is, when the compressor including piston assembly 12 is in operation, seal 400 is capable of sealing the gap and preventing lubricant from leaking out of the gap.
In the related art, the ball seat is welded to the piston head. The retainer is welded on the ball seat and is matched with the ball seat to compress the ball head, so that the ball head is limited between the ball seat and the retainer. The ball head is connected with the connecting rod, so that the connection of the piston and the connecting rod is realized. However, due to the axial shrinkage deformation of the welding line between the ball seat and the piston head, the ball seat can generate extrusion force towards the retainer to the ball head, and due to the axial shrinkage deformation of the welding line between the retainer and the ball seat, the retainer can generate extrusion force towards the ball seat to the ball head, so that the ball head is excessively compressed. And the ball head is excessively compressed, so that the friction between the ball head and the retainer and the ball seat is increased, extra friction work is generated when the ball head moves, and the efficiency of the compressor is reduced. In order to reduce friction, the ball and socket joint needs to be pre-ground for hundreds of hours, so that the production efficiency is greatly reduced and the cost is increased.
In the piston assembly 12, the retainer 320 is fixed in the piston skirt 220 by spot welding, and the retainer 320 is fixed in the piston skirt 220, so that the ball head 310 is limited between the piston head 210 and the retainer 320, and thus axial shrinkage deformation (shrinkage deformation in the vertical direction shown in fig. 3) of a welding point between the retainer 320 and the piston skirt 220 does not cause extrusion force of the retainer 320 on the ball head 310 toward the piston head 210 (since force acting on the ball head 310 generated by axial shrinkage deformation of the welding point is the same as force acting on the ball head 310 by the piston head 210, and distance (distance in the vertical direction) between the piston head 210 and the retainer 320 is not substantially changed, axial shrinkage deformation of the welding point between the retainer 320 and the piston skirt 220 does not cause extrusion force of the retainer 320 on the ball head 310 toward the piston head 210), so that excessive friction does not exist between the ball head 310 and the retainer 320 and between the ball head 310 and the piston head 210 Force, the ball 310 will not generate extra friction work during the movement, and the efficiency of the compressor can be effectively prevented from being reduced, so that the compressor can achieve better efficiency, that is, the piston assembly 12 can improve the efficiency of the compressor.
Moreover, compared with a full circle of continuous annular welding line, that is, compared with full welding, both the force generated by the axial shrinkage deformation of the welding point and the force generated by the radial shrinkage deformation of the welding point (the shrinkage deformation in the left-right direction shown in fig. 3) are small, and the radial shrinkage deformation of the welding point basically does not cause the deformation of the piston skirt 220, that is, the radial shrinkage deformation of the welding point basically does not cause the shape of the piston skirt 220 to deviate from the cylindrical shape, that is, the radial shrinkage deformation of the welding point basically does not cause the poor cylindricity of the piston skirt 220. It should be noted that the shape of the piston skirt 220 deviates from a cylindrical shape, i.e., the poorer the cylindricity of the piston skirt 220, the gas leakage may occur in the gap between the piston skirt 220 and the cylinder, and such leakage may reduce the efficiency of the compressor and lead to increased wear of the cylinder (including the piston 200) during operation of the compressor. That is, the piston assembly 12 described above also prevents the shape of the skirt 220 from deviating from a cylindrical shape, thereby further improving the efficiency of the compressor and reducing wear of the cylinder (including the piston 200).
In addition, because the retainer 320 is fixed in the piston skirt 220 by spot welding, a gap between two adjacent welding points is at risk of oil leakage, and the sealing element 400 can seal the gap when the piston 200 works, thereby solving the problem of oil leakage.
In this embodiment, there are a plurality of (greater than or equal to 3) welding points, and the plurality of welding points are arranged at equal intervals and surround the holder 320 for a circle. Specifically, in the present embodiment, the number of the welding spots is 3 to 8. Too few welding points are not favorable for the retainer 320 and the piston skirt 220 to be firmly connected, and too many welding points are relatively complicated to manufacture. Specifically, in the present embodiment, the number of the welding spots is 4. It is understood that in other embodiments, there may be 2 welds.
In the present embodiment, the cage 320 includes a holding portion 322 for supporting the ball 310, a welding portion 324 for welding with the piston skirt 220, and a flat plate portion 326 connecting the holding portion 322 and the welding portion 324. The holding portion 322 and the welding portion 324 are both located on a side of the flat plate portion 326 away from the piston head 210. In this way, axial shrinkage deformation of the welding point between the retainer 320 and the piston skirt 220 can be further prevented, and a pressing force toward the piston head 210 is generated on the ball 310. It is understood that in other embodiments, the flat plate portion 326 may not be flat but may be bent, and the holding portion 322 and the welding portion 324 may be located on different sides of the flat plate portion 326.
In this embodiment, the cage 320, the piston skirt 220 and the piston head 210 enclose a working space, and at least a portion of the ball head 310 is located in the working space. When the compressor including the above-described piston assembly 12 is operated, the lubricating oil can enter and exit the working space. Specifically, in the present embodiment, the ball head 310 has an oil guide passage 312, and the lubricating oil is introduced into the working space through the oil guide passage 312.
In this embodiment, oil guide passage 312 extends along the arrangement direction of retainer 320 and piston head 210. The oil guide passage 312 has one end for insertion of the connecting rod 14 and the other end for guiding the lubricating oil into the working space. At this time, the extending direction of the oil guide passage 312 is substantially the same as the length direction of the connecting rod 14, so that the flow resistance of the lubricating oil is small, and the oil guide passage 312 is more favorable for guiding the oil. It is understood that in other embodiments, the oil guide passage 312 may extend substantially perpendicular to the length of the connecting rod 14.
In the present embodiment, the oil guide passage 312 includes a connection section 312a and an oil guide section 312b connected. The connecting section 312a is used for the insertion of the connecting rod 14, and the inner diameter of the oil guiding section 312b is larger than that of the connecting section 312 a. Therefore, the flow resistance of the lubricating oil is smaller, and the oil guide channel 312 is more beneficial to guiding the oil. It is understood that in other embodiments, the inner diameter of the oil guiding section 312b and the inner diameter of the connecting section 312a may be substantially the same.
In the present embodiment, the connecting rod 14 has an oil supply passage 14 a. After the connecting rod 14 is inserted into the connecting section 312a of the oil guide passage 312, the oil supply passage 14a communicates with the oil guide section 312 b.
In the present embodiment, the seal 400 includes the oil absorbing expansion seal 400, and the oil absorbing expansion seal 400 expands after absorbing the lubricating oil, so that the size increases (the axial and radial sizes increase, that is, the size in the up-down direction and the size in the left-right direction in fig. 3 increase). The oil absorbing expansion seal 400 is arranged in a working space formed by the retainer 320, the piston head 210 and the piston skirt 220. When the oil absorbing expansion seal 400 is not expanded, that is, when the oil absorbing expansion seal 400 does not absorb oil, the oil absorbing expansion seal 400 is spaced from the retainer 320. After the oil absorption expansion sealing element 400 expands, that is, after the oil absorption expansion sealing element 400 absorbs oil, the oil absorption expansion sealing element 400 simultaneously collides with the inner walls of the retainer 320 and the piston skirt 220 to seal the gap. That is, after the oil absorption expansion seal 400 expands, the axial and radial dimensions of the oil absorption expansion seal 400 increase, and the oil absorption expansion seal 400 can contact the inner wall of the piston skirt 220 and the retainer 320 and generate a slight pressure, thereby achieving the effect of sealing the gap.
When the piston assembly 12 is assembled, after the oil absorbing expansion seal 400 is installed on the piston 200, because the oil absorbing expansion seal 400 is not expanded at this time, when the retainer 320 is installed, the retainer 320 is not in contact with the oil absorbing expansion seal 400, so that the installation pressure of the retainer 320 on the ball head 310 can be ensured to be basically constant.
In this embodiment, the oil absorbing expansion seal 400 is a hollow structure with both ends open. The oil-absorbing expansion sealing member 400 is sleeved outside the ball 310, and one end of the oil-absorbing expansion sealing member 400 is connected to the piston head 210, and the other end is adjacent to the holding frame 320. The oil expansion seal 400 divides the working space into a first space 12a and a second space 12b, the first space 12a is located in the oil expansion seal 400, and the second space 12b is located between the outer wall of the oil expansion seal 400 and the inner wall of the piston skirt 220. The oil-absorbing expansion sealing member 400 is provided with an oil guide hole 410, and the oil guide hole 410 communicates the first space 12a and the second space 12 b. The piston skirt 220 is formed with a rim hole 222, and the rim hole 222 communicates the second space 12b with the outside. The first space 12a communicates with an oil guide passage 312 of the ball head 310. That is, the oil guide passage 312, the first space 12a, the oil guide hole 410, the second space 12b and the side hole 222 are sequentially communicated.
Thus, the oil absorption expansion seal 400 can have a relatively large size, which is more beneficial for the oil absorption expansion seal 400 to seal the gap and is also more convenient for installing the oil absorption expansion seal 400. It is understood that in other embodiments, the oil absorbing expansion seal 400 may be annular and disposed on the inner wall of the piston skirt 220.
In the present embodiment, the oil introduction hole 410 is located closer to the piston head 210 than to the side hole 222 when the oil absorbing expansion seal 400 is not expanded. In some embodiments, the oil introduction hole 410 is closer to the piston head 210 than the side hole 222 after the oil absorption expansion seal 400 is expanded. In some embodiments, the oil suction expansion seal 400 is expanded such that the oil guide hole 410 is aligned with the side hole 222.
Specifically, in the present embodiment, the oil guide holes 410 are multiple, and the multiple oil guide holes 410 are divided into several oil guide hole groups. A plurality of oil guide hole groups are arranged at intervals along the circumferential direction of the oil absorption expansion sealing element 400. Each oil guide hole group includes at least one oil guide hole 410. When each oil guide hole group includes two or more oil guide holes 410, the oil guide holes 410 in each group are arranged at intervals along the arrangement direction of the retainer 320 and the piston head 210.
In the present embodiment, the positioning groove 12c is defined between the inner wall of the piston skirt 220 and the holder 320. The edge of the end of the oil expansion seal 400 away from the piston head 210 extends obliquely toward the inner wall of the piston skirt 220, that is, the end of the oil expansion seal 400 away from the piston head 210 is flared. In this way, after the oil absorption expansion seal 400 expands with oil absorption, the obliquely extending edge of the oil absorption expansion seal 400 can be inserted into the positioning groove 12c, thereby enabling better sealing of the gap.
In this embodiment, the material of the oil absorbing expansion seal 400 is oil absorbing expansion rubber (OSR). It is understood that in other embodiments, the oil absorbing expansion seal 400 may be omitted. In this case, the gap may be sealed by a sealant, i.e., the sealing member 400 may also be a sealant. Wherein, the sealant can be epoxy resin glue or polyacrylic acid glue. When the sealing member 400 is a sealing material, the sealing member 400 may seal the gap when the piston 200 is in operation, and the sealing member 400 may also seal the gap when the piston 200 is not in operation. The seal 400 may also strengthen the connection between the cage 320 and the piston skirt 220.
In this embodiment, ball-and-socket joint 300 further includes ball seat 330. Ball seat 330 is located in the workspace and is located on piston head 210. Specifically, in the present embodiment, ball seat 330 is located in first space 12a and is provided on piston head 210. An oil passage 12d is formed between the ball seat 330 and the ball head 310. The oil passing channel 12d communicates the oil guiding channel 312 with the working space, that is, the oil passing channel 12d communicates the first space 12a with the working space. It is understood that ball seat 330 may be omitted from ball-and-socket joint 300 in other embodiments, ball seat 330 may be formed on piston head 210, i.e., piston head 210 may be integrally formed with ball seat 330 in other embodiments.
In this embodiment, ball seat 330 is fixed to piston head 210 by welding.
In this embodiment, as shown in fig. 4, an oil guiding groove 332 is formed on a surface of the ball seat 330 near the ball head 310, and the oil guiding groove 332 is used for forming the oil passing channel 12 d. Thus, the oil passing passage 12d is very conveniently formed. It is understood that in other embodiments, the oil guide groove 332 may be omitted, and in this case, the ball seat 330 is in clearance fit with the ball head 310, and the oil passing passage 12d may also be formed.
In this embodiment, the ball seat 330 has an oil guide area 330a facing one end of the oil guide passage 312. The oil guide grooves 332 are plural, and one end of the oil guide grooves 332 converge at the oil guide area 330 a. Therefore, oil is more favorably guided. Specifically, in the present embodiment, the oil guide grooves 332 are disposed at equal central angles with respect to the oil guide area 330 a. Therefore, the oil guide device is more beneficial to uniformly guiding oil. More specifically, in the present embodiment, there are three oil guide grooves 332.
The present invention further provides a compressor, which includes a piston rod device 10, and the specific structure of the piston rod device 10 refers to the above embodiments, and since the piston rod device 10 adopts all technical solutions of all the above embodiments, at least all beneficial effects brought by the technical solutions of the above embodiments are achieved, and are not described in detail herein. The compressor can be applied to household appliances such as refrigerators, air conditioners and the like.
The above description is only an alternative embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications and equivalents of the present invention, which are made by the contents of the present specification and the accompanying drawings, or directly/indirectly applied to other related technical fields, are included in the scope of the present invention.
Claims (12)
1. A piston assembly, comprising:
the piston is provided with a piston head and a piston skirt, the piston skirt is of a hollow structure with two open ends, and the piston head is arranged at one open end of the piston skirt;
the ball-and-socket joint is provided with a ball head and a retainer, the retainer is fixed in the piston skirt in a spot welding manner, the ball head is limited between the piston head and the retainer, a gap between two adjacent welding points is formed between the retainer and the piston skirt, and the ball head is used for being connected with a connecting rod; and
a seal capable of sealing the void when the piston is in operation.
2. The piston assembly of claim 1, wherein said weld points are a plurality of said weld points being equally spaced around said piston skirt.
3. The piston assembly of claim 1, wherein the retainer includes a retaining portion for supporting the ball head, a weld portion for welding with the piston skirt, and a flat plate portion connecting the retaining portion and the weld portion, the retaining portion and the weld portion each being located on a side of the flat plate portion away from the piston head.
4. The piston assembly of claim 1, wherein the cage, the skirt and the head enclose a working space, and the ball head has an oil guide channel for supplying oil to the working space, the oil guide channel extending in a direction of arrangement of the cage and the head.
5. The piston assembly of claim 4, wherein the oil guide passage includes a connection section for insertion of the connecting rod and an oil guide section having an inner diameter larger than that of the connection section, which are connected.
6. The piston assembly of claim 4, wherein said seal includes an oil absorbing expansion seal disposed in said working space, said oil absorbing expansion seal being spaced from said cage when unexpanded, and said oil absorbing expansion seal simultaneously interfering with said cage and an inner wall of said piston skirt after expansion to seal said gap.
7. The piston assembly of claim 6, wherein the oil-absorbing expansion seal is a hollow structure with two open ends, the oil-absorbing expansion seal is sleeved outside the ball head, one end of the oil-absorbing expansion seal is connected with the piston head, the other end of the oil-absorbing expansion seal is adjacent to the retainer, the oil-absorbing expansion seal divides the working space into a first space located inside the oil-absorbing expansion seal and a second space located between the oil-absorbing expansion seal and the piston skirt, the oil-absorbing expansion seal is provided with an oil guide hole, the piston skirt is provided with a side hole, and the oil guide channel, the first space, the oil guide hole, the second space and the side hole are sequentially communicated.
8. The piston assembly as set forth in claim 7, wherein a positioning groove is defined between the inner wall of the skirt and the holder, and an edge of an end of the oil expansion seal remote from the piston head is obliquely extended toward the inner wall of the skirt, and the obliquely extended edge of the oil expansion seal is inserted into the positioning groove after the expansion.
9. The piston assembly of claim 4, wherein the ball-and-socket joint further includes a ball seat disposed in the working space and on the piston head, and an oil passage communicating the oil guide passage and the working space is provided between the ball seat and the ball head.
10. The piston assembly of claim 9, wherein said ball seat has an oil guide area opposite to one end of said oil guide passage, said ball seat has a plurality of oil guide grooves for forming said oil passage, and one end of said plurality of oil guide grooves converges at said oil guide area.
11. The piston assembly of claim 1 wherein said seal comprises a sealant disposed at said gap.
12. A compressor, comprising:
the piston assembly of any one of claims 1-11; and
and the connecting rod is connected with the ball head.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122942297.1U CN216518497U (en) | 2021-11-24 | 2021-11-24 | Piston assembly and compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122942297.1U CN216518497U (en) | 2021-11-24 | 2021-11-24 | Piston assembly and compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN216518497U true CN216518497U (en) | 2022-05-13 |
Family
ID=81462118
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122942297.1U Active CN216518497U (en) | 2021-11-24 | 2021-11-24 | Piston assembly and compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN216518497U (en) |
-
2021
- 2021-11-24 CN CN202122942297.1U patent/CN216518497U/en active Active
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