CN212838342U - Cylinder assembly, compressor and refrigeration equipment - Google Patents
Cylinder assembly, compressor and refrigeration equipment Download PDFInfo
- Publication number
- CN212838342U CN212838342U CN202021218608.9U CN202021218608U CN212838342U CN 212838342 U CN212838342 U CN 212838342U CN 202021218608 U CN202021218608 U CN 202021218608U CN 212838342 U CN212838342 U CN 212838342U
- Authority
- CN
- China
- Prior art keywords
- cylinder
- groove
- wall
- width direction
- rotary piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The application belongs to the technical field of compressors, and particularly relates to an air cylinder assembly, a compressor and refrigeration equipment. The cylinder assembly comprises a cylinder, a slip sheet, a crankshaft and a rotary piston, the crankshaft drives the rotary piston to eccentrically rotate, a sliding groove is radially formed in the inner wall of the cylinder along the inner wall, the slip sheet is slidably arranged in the sliding groove, one end of the slip sheet is abutted to the outer wall of the rotary piston, a groove communicated with the sliding groove is formed in the inner wall of the cylinder, and the groove meets the following relational expression along the radial depth of the cylinder: t is more than or equal to 2emm and more than or equal to 0.02 mm. The refrigerator oil enters a partial area of the sliding groove through the groove, so that the crankshaft can smoothly rotate in the cylinder, and the operation efficiency of the cylinder assembly is improved. Through making the radial degree of depth of recess along the cylinder be greater than or equal to 0.02mm, and the bent axle eccentric quantity of less than or equal to twice, just so when guaranteeing that refrigerator oil can smoothly pass through the recess, also effectively avoided the recess to set up too deeply to the bulk strength who has also guaranteed the cylinder does not descend.
Description
Technical Field
The application belongs to the technical field of compressors, and particularly relates to an air cylinder assembly, a compressor and refrigeration equipment.
Background
The compressor is widely applied to refrigeration equipment as a fluid machine for converting low-pressure gas into high-pressure gas, and in the compressor, a large amount of refrigerating machine oil is usually reserved in a cylinder, so that the friction loss among kinematic pairs such as a crankshaft, a rotary piston, the inner wall of the cylinder, a bearing and the like in the cylinder is reduced, and meanwhile, the effects of cooling and the like are also achieved. However, the refrigerating machine oil present in the cylinder may cause an obstruction to the movement of the crankshaft in the cylinder, which may result in an increase in power consumption of the compressor. In order to solve the above problems, an oil guiding groove needs to be formed on the inner wall of the cylinder, which may result in the overall strength of the cylinder being reduced.
SUMMERY OF THE UTILITY MODEL
An object of the application is to provide a cylinder subassembly, compressor and refrigeration plant, aim at guaranteeing under the not obvious prerequisite that descends of cylinder bulk strength, solve the cylinder and persist refrigerating machine oil and lead to the technical problem of compressor consumption increase.
In order to achieve the purpose, the technical scheme adopted by the application is as follows:
in a first aspect: the cylinder component comprises a cylinder, a sliding piece, a crankshaft and a rotary piston, wherein the crankshaft extends into the cylinder and is used for driving the rotary piston to eccentrically rotate in the cylinder, a sliding groove is formed in the inner wall of the cylinder along the radial direction of the cylinder, the sliding piece is arranged in the sliding groove in a sliding mode, one end of the sliding piece is abutted to the outer wall of the rotary piston, a groove communicated with the sliding groove is formed in the inner wall of the cylinder, the groove starts from the junction of the sliding groove and the inner wall of the cylinder and extends towards the rotating direction of the crankshaft, and the radial depth of the groove along the cylinder meets the following relational expression:
2emm≥t≥0.02mm；
wherein t represents a depth of the groove in a radial direction of the cylinder, and e represents an eccentric amount of the crankshaft.
Optionally, a suction hole is formed in the inner wall of the cylinder at a position spaced from the sliding groove, and a length of the groove extending along the circumferential direction of the cylinder satisfies the following relational expression:
L1≥L＞0；
wherein L represents a length of the groove extending in a circumferential direction of the cylinder, L1The distance between the junction of the sliding chute and the inner wall of the cylinder and the junction of the air suction hole and the inner wall of the cylinder is represented.
Optionally, a suction hole is formed in the inner wall of the cylinder at a position spaced from the sliding groove, and a length of the groove extending along the circumferential direction of the cylinder satisfies the following relational expression:
L2+L1≥L＞L1；
wherein L represents a length of the groove extending in a circumferential direction of the cylinder, L2The aperture of the boundary between the suction hole and the inner wall of the cylinder is shown.
Optionally, the length of the groove in the cylinder width direction satisfies the following relation:
m≥m0＞0；
wherein m is0Denotes the length of the groove in the width direction of the cylinder, and m denotes the width of the cylinder.
Alternatively, a distance between one side of the groove in the cylinder width direction and an adjacent side of the cylinder in the width direction thereof is defined as m1, a distance between the opposite other side of the groove in the cylinder width direction and the adjacent side of the cylinder in the width direction thereof is defined as m2, and m1, m2 and m satisfy the following relations:
m＞m1≥0；
m＞m2≥0。
optionally, the groove is located in a middle region in the cylinder width direction.
Optionally, the groove is a milled groove.
Optionally, the contour shape of a cross section of the groove in the width direction of the cylinder is a semicircle, a rectangle, or a polygon.
The application has at least the following beneficial effects: the application provides a cylinder component, during operation, the bent axle that stretches into in the cylinder drives rotary piston and rotates for cylinder eccentric, and then produces centrifugal force, in order to drive the gleitbretter and throw away from the spout, along with the periodic motion of gleitbretter, the space in the cylinder also can produce the volume change, and then realize the compression to the air in the cylinder, when cylinder component moves, rotary piston's outer wall and the inner wall of cylinder constitute the crescent space, rotary piston when rotating to spout department, rotary piston's outer wall and the groove edge of spout just can be in the cusp department of crescent space, and cusp department space is little, the refrigerating machine oil pressure that is in it is great, then through seting up the recess at the cylinder inner wall, and make the recess begin in the juncture of spout and cylinder inner wall and extend towards rotary piston's direction of rotation, the existence of recess is equivalent to seting up the space that releases refrigerating machine oil at the cusp department, when the rotary piston rotates, refrigerating machine oil can enter a groove extending along the rotating direction of the rotary piston along the extrusion of the rotary piston, and enters a partial area of the sliding groove through the groove, so that the resistance applied to the outer wall of the crankshaft at the tooth tip is released, the crankshaft can rotate in the cylinder more smoothly, the power consumption of the cylinder assembly is reduced remarkably, and the operating efficiency of the cylinder assembly is improved. And through making the radial degree of depth of recess along the cylinder be more than or equal to 0.02mm, and the bent axle eccentric quantity of less than or equal to twice, just so when guaranteeing that refrigerator oil can smoothly pass through the recess, also effectively avoided the recess to set up too deeply to the bulk strength who has also guaranteed the cylinder does not descend.
In a second aspect: a compressor is provided, which comprises the cylinder assembly.
The application provides a compressor, owing to including foretell cylinder assembly, and foretell cylinder assembly can also promote its operating efficiency when guaranteeing cylinder intensity, so also make the compressor including above-mentioned cylinder assembly when guaranteeing the structural reliability, also promoted its work efficiency.
In a third aspect: there is provided a refrigeration apparatus comprising the compressor described above.
The application provides a refrigeration plant, owing to including foretell compressor, and foretell compressor can release the resistance that refrigerator oil applied to rotary piston through the recess of seting up near the spout of cylinder, guarantees cylinder intensity simultaneously, so just so also showing work efficiency and the operational reliability who has promoted refrigeration plant.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the embodiments or the prior art descriptions will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise.
FIG. 1 is a first schematic structural view of a cylinder assembly according to an embodiment of the present disclosure;
FIG. 2 is an enlarged view of a portion of FIG. 1 at A;
FIG. 3 is a schematic structural diagram of a second cylinder assembly provided in the embodiments of the present application;
FIG. 4 is an enlarged partial view taken at B in FIG. 3;
FIG. 5 is a third schematic structural view of a cylinder assembly provided in an embodiment of the present application;
FIG. 6 is an enlarged partial view at C of FIG. 5;
FIG. 7 is a cross-sectional view taken along line D-D of FIG. 5;
FIG. 8 is another cross-sectional view taken along line D-D of FIG. 5;
fig. 9 is a bar graph comparing COP% of a cylinder assembly according to an embodiment of the present invention and a cylinder assembly according to the related art.
Wherein, in the figures, the respective reference numerals:
10-cylinder 11-sliding vane 12-rotary piston
13-chute 14-groove 15-suction hole
16-refrigerator oil.
Detailed Description
Reference will now be made in detail to embodiments of the present application, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to fig. 1-9 are exemplary and intended to be used to illustrate the present application and should not be construed as limiting the present application.
In the description of the present application, it is to be understood that the terms "length," "width," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like, as used herein, refer to an orientation or positional relationship indicated in the drawings, which is for convenience and simplicity of description, and does not indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and thus, is not to be considered as limiting.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are 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 one or more of that feature. In the description of the present application, "a plurality" means two or more unless specifically limited otherwise.
In this application, unless expressly stated or limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can include, for example, fixed connections, removable connections, or integral parts; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.
As shown in fig. 1 to 3, an embodiment of the present application provides a cylinder assembly, which is applied to a compressor, where the compressor is applied to a refrigeration apparatus, and the compressor may be a rotary compressor. The cylinder assembly includes a cylinder 10, a sliding vane 11, a crankshaft (not shown) and a rotary piston 12, wherein the crankshaft extends into the cylinder 10 and is used for driving the rotary piston 12 to eccentrically rotate in the cylinder 10, specifically, eccentrically rotate with respect to the center of the cylinder 10. The inner wall of cylinder 10 has seted up spout 13 along its radial, and gleitbretter 11 slides and sets up in spout 13, and the outer wall looks butt of one end and rotary piston 12 of gleitbretter 11, and wherein, but gleitbretter 11 elastic connection is in spout 13 to with rotary piston 12's outer wall elasticity butt.
Specifically, the inner wall of the cylinder 10 is opened with a groove 14 communicating with the sliding groove 13, and the groove 14 starts at the intersection of the sliding groove and the inner wall of the cylinder 10 (as shown by point E in fig. 2) and extends toward the rotation direction of the rotary piston 12 (in the embodiment of the present application, the rotation direction of the rotary piston 12 may be a counterclockwise direction).
Specifically, the specific structure of the cylinder assembly may be: the inner wall of the cylinder 10 is provided with a plurality of sliding grooves 13 at intervals along the radial direction, the number of the sliding pieces 11 corresponds to a plurality of sliding grooves 13, the rotary piston 12 periodically pushes a plurality of sliding pieces 11 to slide out of the sliding grooves 13 and contact the inner wall of the cylinder 10 when rotating, then the plurality of sliding grooves 13 can separate the space in the cylinder 10 into a plurality of element spaces, and along with the rotation of the crankshaft 12, the volume of each element containing space can be changed from large to small, so that the effective compression of air in the cylinder 10 can be realized.
The cylinder assembly provided by the embodiments of the present application is further described below: in the cylinder assembly provided by the embodiment of the application, during operation, the crankshaft extending into the cylinder 10 drives the rotary piston 12 to eccentrically rotate relative to the cylinder 10, so as to generate centrifugal force, so as to drive the sliding vane 11 to be thrown out from the sliding groove 13, so that the sliding vane is tightly attached to the inner wall of the cylinder 10, along with the periodic motion of the sliding vane 11, the space in the cylinder 10 also generates volume change, so as to compress air in the cylinder 10, when the cylinder assembly operates, a crescent-shaped space is formed by the outer wall of the rotary piston 12 and the inner wall of the cylinder 10, when the rotary piston 12 rotates to the sliding groove 13, the outer wall of the rotary piston 12 and the groove edge of the sliding groove 13 are located at the cusp of the crescent-shaped space, the space at the cusp is small, the oil pressure of the refrigerating machine oil 16 located therein is large, then, by forming the groove 14 on the inner wall of the cylinder 10, and enabling the groove 14 to start at the junction of the sliding groove 13 and the inner wall, the existence of the groove 14 is equivalent to opening up a space for releasing the refrigerating machine oil 16 at the cusp, when the rotary piston 12 rotates, the refrigerating machine oil 16 can enter the groove 14 extending along the rotating direction of the rotary piston 12 under the extrusion of the rotary piston 12 and enter a partial area of the sliding chute 13 through the groove 14, so that the resistance applied to the outer wall of the rotary piston 12 at the cusp is released, the rotary piston 12 can rotate in the cylinder 10 more smoothly, the power consumption of the cylinder assembly is remarkably reduced, and the operating efficiency of the cylinder assembly is improved. And through making recess 14 along the radial degree of depth of cylinder 10 more than or equal to 0.02mm, and be less than or equal to twice bent axle eccentric magnitude, just so guarantee that refrigerator oil 16 can smoothly pass through recess 14 simultaneously, also effectively avoided recess 14 to set up too deeply to the bulk strength who has also guaranteed cylinder 10 does not descend.
The application provides a compressor, owing to including foretell cylinder assembly, and foretell cylinder assembly can also promote its operating efficiency when guaranteeing cylinder 10 intensity, so also make the compressor including above-mentioned cylinder assembly when guaranteeing the structural reliability, also promoted its work efficiency.
The refrigeration equipment provided by the embodiment of the application comprises the compressor, and the compressor can release the resistance applied by the refrigerating machine oil 16 to the rotating piston 12 through the groove 14 arranged near the chute 13 of the cylinder 10, and meanwhile, the strength of the cylinder 10 is ensured, so that the working efficiency and the working reliability of the refrigeration equipment are also obviously improved.
In other embodiments of the present application, as shown in fig. 1, 3 and 5, the inner wall of the cylinder 10 is provided with a suction hole 15 at a position spaced from the sliding slot 13, and the length of the groove 14 extending along the circumferential direction of the cylinder 10 satisfies the following relation:
L1≥L＞0；
wherein L denotes the length of the groove 14 extending in the circumferential direction of the cylinder 10, L1Showing the sliding channel 13 and the inner wall of the cylinderThe distance between the boundary (indicated by point E in fig. 2, 4 and 6) and the boundary (indicated by point F in fig. 2, 4 and 6) of the suction hole 15 and the inner wall of the cylinder 10.
Specifically, as shown in fig. 2, as a first design manner of the groove 14, by making L1L is more than 0, which means that the length of the groove 14 extending along the circumferential direction of the cylinder 10 can occupy the area between the sliding chute 13 and the air suction hole 15, and when the groove 14 completely occupies the area between the sliding chute 13 and the air suction hole 15, the length of the groove 14 is not excessively long, so that the effective drainage of the refrigerating machine oil 16 can be realized, and the refrigerating machine oil 16 partially flows into the sliding chute 13 through the groove 14 under the extrusion action of the rotary piston 12, so as to reduce the resistance exerted by the refrigerating machine oil on the outer wall of the rotary piston 12, and further improve the working efficiency of the cylinder assembly.
In other embodiments of the present application, as shown in fig. 1, 3 and 5, the inner wall of the cylinder 10 is provided with a suction hole 15 at a position spaced from the sliding slot 13, and the length of the groove 14 extending along the circumferential direction of the cylinder 10 satisfies the following relation:
L2+L1≥L＞L1；
wherein L denotes the length of the groove 14 extending in the circumferential direction of the cylinder 10, L2The hole diameter at the boundary between the suction hole 15 and the inner wall of the cylinder 10 is shown.
Specifically, as a second design of the groove 14, L, as shown in fig. 42+L1＞L＞L1It means that the groove 14 may extend along the circumferential direction of the cylinder 10 to a partial region where the suction hole 15 and the inner wall of the cylinder 10 meet, so that the refrigerating machine oil 16 may partially flow into the suction hole 15 through the groove 14 and partially flow into the sliding groove 13 through the groove 14 under the squeezing action of the rotary piston 12, thereby further reducing the resistance exerted by the rotary piston 12 on the outer wall, making the rotation resistance of the rotary piston 12 smaller, and further improving the working efficiency of the cylinder assembly.
As shown in fig. 6, and as a third design of the recess 14, L2+L1＝L＞L1By this is meant that the groove 14 may extend completely in the circumferential extension of the cylinder 10 to the suction opening 15 and the cylinder 10, more refrigerant oil 16 can be caused to flow into the suction hole 15 by the drainage of the groove 14, thereby further improving the working efficiency of the cylinder assembly.
The third design mode also represents the limit design length of the groove 14, so that the length of the groove 14 along the radial direction of the cylinder 10 can be prevented from exceeding the area of the air suction hole 15 along the radial direction of the cylinder 10, and further the air suction cooling capacity of the air suction hole 15 is prevented from being reduced.
In other embodiments of the present application, as shown in fig. 7 and 8, the length of the groove 14 in the width direction of the cylinder 10 satisfies the following relationship:
m≥m0＞0；
wherein m is0The length of the groove 14 in the width direction of the cylinder 10 is shown, and m represents the width of the cylinder 10.
Specifically, in the above three design manners of the groove 14, the length of the groove 14 along the width direction of the cylinder 10 is required to be less than or equal to the width of the cylinder 10, which also means that the groove 14 can penetrate through the cylinder 10 along the width direction of the cylinder 10 or occupy a partial area of the width direction of the cylinder 10, and preferably the groove 14 completely penetrates through the cylinder 10, so that the refrigerating machine oil 16 can flow into the sliding chute 13 or the air suction hole 15 via the groove 14 as much as possible, thereby further reducing the rotation resistance of the rotary piston 12 and improving the working efficiency of the cylinder assembly.
In other embodiments of the present application, as shown in fig. 7, a distance between one side of the groove 14 in the width direction of the cylinder 10 and an adjacent side of the cylinder 10 in the width direction thereof is defined as m1, a distance between the opposite other side of the groove 14 in the width direction of the cylinder 10 and the adjacent side of the cylinder 10 in the width direction thereof is defined as m2, and m1, m2 and m satisfy the following relations:
m＞m1≥0；
m＞m2≥0。
specifically, when the groove 14 occupies a partial area in the width direction of the cylinder 10, a distance between both sides in the width direction of the cylinder 10 and the groove 14 is generated: m1 and m2, where m1 and m2 may be equal, which means that the groove 14 occupies the middle area in the width direction of the cylinder 10, and m1 and m2 may be unequal, which means that the groove 14 is located near one of the two sides in the width direction of the cylinder 10. Preferably, the groove 14 may be located at a middle region in a width direction of the cylinder 10, which may allow the refrigerating machine oil 16 to flow into the chute 13 and/or the suction hole 15 via the groove 14 more smoothly.
In other embodiments of the present application, the groove 14 is a milled groove. Specifically, the grooves 14 are formed by milling, so that on one hand, the efficiency of the milling operation is improved, and the forming efficiency of the grooves 14 can be remarkably improved. On the other hand, due to the fact that milling machining can achieve effective machining of curved surfaces and surfaces with complex configurations, the diversity of the cross section shapes of the grooves 14 can be enriched. Meanwhile, the milling process can also effectively control the processing cost of the groove 14.
In other embodiments of the present application, the cross-sectional profile of the groove 14 in the width direction of the cylinder 10 is semicircular, rectangular, or polygonal. Specifically, the cross section of the groove 14 in the width direction of the cylinder 10 may be selected to be semicircular, rectangular, or polygonal according to practical circumstances.
As shown in fig. 9, in the example of the present application, the cylinder assembly without grooves (shown by abscissa K in fig. 9) and the cylinder assembly with grooves of the first design (shown by abscissa K1 in fig. 9), the cylinder assembly with grooves of the second design (shown by abscissa K2 in fig. 9), and the cylinder assembly with grooves of the third design (shown by abscissa K3 in fig. 9) were compared to obtain the COP percentages (ratio of cooling capacity to input feed) of the four cylinder assemblies, as shown in fig. 9, in the transverse comparison, the COP percentage of the cylinder assembly with the grooved second design is higher than that of the cylinder assembly without the grooves by 0.9%, and it can be seen that the cylinder assembly with the grooved second design has the highest working efficiency.
The present invention is not intended to be limited to the particular embodiments shown and described, but is to be accorded the widest scope consistent with the principles and novel features herein disclosed.
Claims (10)
1. A cylinder assembly, characterized by: including cylinder, gleitbretter, bent axle and rotary piston, the bent axle stretches into in the cylinder and be used for driving rotary piston is in eccentric rotation in the cylinder, the inner wall of cylinder has radially seted up the spout along it, the gleitbretter slide set up in the spout, just the one end of gleitbretter with rotary piston's outer wall looks butt, the inner wall of cylinder seted up with the recess that the spout is linked together, the recess begins the spout with the juncture of cylinder inner wall and orientation the direction of rotation of bent axle extends, the recess is followed the radial degree of depth of cylinder satisfies following relational expression:
2emm≥t≥0.02mm；
wherein t represents a depth of the groove in a radial direction of the cylinder, and e represents an eccentric amount of the crankshaft.
2. The cylinder assembly of claim 1, wherein: the inner wall of the cylinder is provided with air suction holes at positions spaced from the sliding groove, and the length of the groove extending along the circumferential direction of the cylinder meets the following relational expression:
L1≥L＞0；
wherein L represents a length of the groove extending in a circumferential direction of the cylinder, L1The distance between the junction of the sliding chute and the inner wall of the cylinder and the junction of the air suction hole and the inner wall of the cylinder is represented.
3. The cylinder assembly of claim 1, wherein: the inner wall of the cylinder is provided with air suction holes at positions spaced from the sliding groove, and the length of the groove extending along the circumferential direction of the cylinder meets the following relational expression:
L2+L1≥L＞L1；
wherein L represents a length of the groove extending in a circumferential direction of the cylinder, L2The aperture of the boundary between the suction hole and the inner wall of the cylinder is shown.
4. The cylinder assembly of claim 2 or 3, wherein: the length of the groove along the width direction of the cylinder meets the following relational expression:
m≥m0＞0；
wherein m is0Denotes the length of the groove in the width direction of the cylinder, and m denotes the width of the cylinder.
5. The cylinder assembly of claim 4, wherein: a distance between one side of the groove in the cylinder width direction and an adjacent side of the cylinder in the width direction thereof is defined as m1, a distance between the opposite other side of the groove in the cylinder width direction and the adjacent side of the cylinder in the width direction thereof is defined as m2, and m1, m2 and m satisfy the following relations:
m＞m1≥0；
m＞m2≥0。
6. the cylinder assembly as set forth in any one of claims 1 to 3, wherein: the groove is located in a middle area in the width direction of the cylinder.
7. The cylinder assembly as set forth in any one of claims 1 to 3, wherein: the groove is a milling groove.
8. The cylinder assembly as set forth in any one of claims 1 to 3, wherein: the outline shape of the cross section of the groove along the width direction of the cylinder is semicircular, rectangular or polygonal.
9. A compressor, characterized by: comprising a cylinder assembly according to any one of claims 1 to 8.
10. A refrigeration apparatus, characterized by: comprising the compressor of claim 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021218608.9U CN212838342U (en) | 2020-06-28 | 2020-06-28 | Cylinder assembly, compressor and refrigeration equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021218608.9U CN212838342U (en) | 2020-06-28 | 2020-06-28 | Cylinder assembly, compressor and refrigeration equipment |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN212838342U true CN212838342U (en) | 2021-03-30 |
Family
ID=75178078
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202021218608.9U Active CN212838342U (en) | 2020-06-28 | 2020-06-28 | Cylinder assembly, compressor and refrigeration equipment |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN212838342U (en) |
-
2020
- 2020-06-28 CN CN202021218608.9U patent/CN212838342U/en active Active
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1114043C (en) | Vortex compressor | |
| JP6724053B2 (en) | Positive displacement machine by spiral principle, method for driving positive displacement machine, positive displacement spiral, vehicle air conditioner and vehicle | |
| EP2177765B1 (en) | Scroll compressor and refrigerating machine having the same | |
| CN102472273A (en) | Scroll compressor | |
| CN110520624B (en) | Rotary compressor | |
| KR101681590B1 (en) | Scroll compressor | |
| CN212838342U (en) | Cylinder assembly, compressor and refrigeration equipment | |
| CN111878395A (en) | Scroll compressor having a plurality of scroll members | |
| CN101542125B (en) | Fluid machine | |
| EP2042741A2 (en) | Two-stage compression rotary compressor | |
| CN102734168A (en) | Oil supply hole structure of rotary compressor eccentric crankshaft | |
| CN105909498B (en) | Two level stroke type rotary compressor | |
| CN205918605U (en) | Sliding vane type compressor and domestic appliance | |
| CN210461058U (en) | Rotary compressor capable of independently compressing | |
| CN207830127U (en) | The compression mechanism of screw compressor | |
| CN1637299A (en) | Screw compressor | |
| GB2113774A (en) | Electric compressor | |
| CN211343689U (en) | Compressor crankshaft capable of improving reliability | |
| CN209510547U (en) | A kind of axial plunger pump | |
| CN220791503U (en) | Superimposed sliding vane compressor with oil drainage pressure structure | |
| CN217842009U (en) | Novel rotary compressor pumping structure | |
| CN218816975U (en) | Compressor pump body and compressor | |
| JP5748723B2 (en) | Hermetic rotary compressor and refrigeration cycle apparatus | |
| CN218030619U (en) | Compression assembly and compressor with same | |
| CN209637958U (en) | A kind of swash-plate air conditioner compressor for automobile exhaust oil-returning structure |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |