CN112032052A - Three-cylinder rolling rotor compressor - Google Patents
Three-cylinder rolling rotor compressor Download PDFInfo
- Publication number
- CN112032052A CN112032052A CN201910483111.5A CN201910483111A CN112032052A CN 112032052 A CN112032052 A CN 112032052A CN 201910483111 A CN201910483111 A CN 201910483111A CN 112032052 A CN112032052 A CN 112032052A
- Authority
- CN
- China
- Prior art keywords
- cylinder
- crankshaft
- cylinders
- piston
- rolling rotor
- 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.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with or adaptation to specific driving engines or motors
Abstract
The invention relates to the technical field of compressors, in particular to a three-cylinder rolling rotor type compressor, which comprises: the crankshaft is provided with a long shaft part and three eccentric parts which are sequentially arranged along the axial direction, the axes of the three eccentric parts are distributed on a circle which takes the axis of the crankshaft as the center of a circle, and the included angle between the axes of two adjacent eccentric parts is 120 degrees; the motor component is sleeved outside the long shaft part; the three pistons are respectively sleeved outside the three eccentric parts; the three cylinders are respectively sleeved outside the three pistons; the side wall of each cylinder is provided with a blade, the blades rotate along with the motor assembly to drive the crankshaft to rotate, the crankshaft drives the piston to eccentrically rotate in the cylinder, the blades abut against the piston to divide a compression space between the cylinder and the piston into an air suction cavity and an air exhaust cavity, and the air suction cavity volume and the air exhaust cavity volume of the three cylinders are the same at the same time. The invention can realize that the acting force of the resultant force of the gas in the three cylinders on the crankshaft is constantly zero, reduce the bending degree of the crankshaft and improve the efficiency and the reliability of the compressor.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a three-cylinder rolling rotor type compressor.
Background
With the continuous development of compressor technology, it is more and more important to further improve the energy efficiency of the compressor. Meanwhile, the development trend of the rolling rotor compressor is developing toward a large capacity direction, and the rolling rotor compressor competes with a large capacity scroll compressor.
At present, the rolling rotor type compressor mainly takes a single rotor type structure and a double rotor type structure as main parts. Fig. 1 shows a schematic structural diagram of a conventional single-rotor compressor, which mainly comprises a housing 11 ', a motor 12', a crankshaft 13 ', an upper muffler 14', an upper cylinder cover 15 ', a cylinder 16', a piston 17 ', a lower cylinder cover 18', a lower muffler 19 'and a reservoir 10'. The crankshaft 13 ' is driven by the motor 12 ' to rotate, and the crankshaft 13 ' drives the piston 17 ' to compress the cooling medium in the cylinder 16 ' so as to realize gas pressurization. The suction port 160 'of the cylinder 16' is located at the side of the cylinder 16 'and is connected to the accumulator 10'.
Fig. 2 shows a schematic structural diagram of a conventional dual-rotor compressor, which mainly includes a casing 11 ', a motor 12 ', a crankshaft 13 ', an upper muffler 14 ', an upper cylinder cover 15 ', an upper cylinder 161 ', an upper piston 171 ', a middle plate 158 ', a lower cylinder 162 ', a lower piston 172 ', a lower cylinder cover 18 ', a lower muffler 19 ', and a reservoir 10 '. The upper piston 171 ' and the lower piston 172 ' are disposed 180 ° apart, and the suction port 1610 ' of the upper cylinder 161 ' and the suction port 1620 ' of the lower cylinder 162 ' are located on the same side of the compressor, and are connected to the accumulator 10 '.
Fig. 3 shows a structural schematic diagram of an upper cylinder and a lower cylinder in a present dual-rotor compressor. As can be seen from fig. 3, (a) a compression space between the upper cylinder 161 'and the upper piston 171' is partitioned into a suction chamber 1617 'and a discharge chamber 1618' by the vane 1611 'of the upper cylinder 161', and (b) a compression space between the lower cylinder 162 'and the lower piston 172' is partitioned into a suction chamber 1627 'and a discharge chamber 1628' by the vane 1621 'of the lower cylinder 162'. Since the upper piston 171 'and the lower piston 172' are disposed different by 180 °, when the center point of the upper piston 171 'is rotated by an angle θ, the center point of the lower piston 172' is rotated by (θ +180 °). With this arrangement, the suction port 1610 'of the upper cylinder 161' and the suction port 1620 'of the lower cylinder 162' are located on the same side of the compressor, and the rotation angle of the center point of the upper piston 171 'is not identical to that of the center point of the lower piston 172', so that the volume of the suction chamber 1617 'of the upper cylinder 161' is always not identical to that of the suction chamber 1627 'of the lower cylinder 162', and the volume of the discharge chamber 1618 'of the upper cylinder 161' is always not identical to that of the discharge chamber 1628 'of the lower cylinder 162'.
Further, since the volume of the suction chamber 1617 ' of the upper cylinder 161 ' is different from the volume of the suction chamber 1627 ' of the lower cylinder 162 ' at any time, the resultant force of the gas of the upper cylinder 161 ' and the lower cylinder 162 ' on the crankshaft 13 ' is large, which causes the bending deformation of the crankshaft 13 ' to be large, and the bending deformation of the crankshaft 13 ' may have an adverse effect on the fit clearance of each part of the pump body of the compressor, resulting in the reduction of the reliability and performance of the compressor.
It is to be noted that the information disclosed in the above background section is only for enhancement of understanding of the background of the present invention and therefore may include information that does not constitute prior art known to a person of ordinary skill in the art.
Disclosure of Invention
In view of the above, the present invention provides a three-cylinder rolling rotor compressor, which can improve the efficiency and reliability of the compressor by improving the stress on the crankshaft.
According to an aspect of the present invention, there is provided a three-cylinder rolling rotor type compressor, including: the crankshaft is provided with a long shaft part and three eccentric parts which are sequentially arranged along the axial direction, the axes of the three eccentric parts are distributed on a circle which takes the axis of the crankshaft as the circle center, and the included angle between the axes of two adjacent eccentric parts is 120 degrees; the motor assembly is sleeved outside the long shaft part; the three pistons are respectively sleeved outside the three eccentric parts; the three cylinders are respectively sleeved outside the three pistons; the side wall of each cylinder is provided with a blade, the crankshaft is driven to rotate along with the motor assembly, the crankshaft drives the piston to eccentrically rotate in the cylinder, the blade abuts against the piston to divide a compression space between the cylinder and the piston into an air suction cavity and an air exhaust cavity, and the air suction cavities of the three cylinders have the same volume and the same volume.
Preferably, in the above three-cylinder rolling rotor compressor, the side wall of each cylinder is provided with an air inlet and an air outlet on two sides of the vane, and an included angle α between the air inlets of two adjacent cylinders satisfies: alpha is more than or equal to 5 degrees and less than or equal to 120 degrees.
Preferably, in the three-cylinder rolling rotor compressor, the included angle α is equal to 120 °, and the volume of the compression space of each cylinder is equal.
Preferably, in the three-cylinder rolling rotor compressor, three of the cylinders are equal in size and three of the pistons are equal in size.
Preferably, in the three-cylinder rolling rotor compressor, the distance between two adjacent eccentric portions in the axial direction is equal.
Preferably, the three-cylinder rolling rotor compressor further comprises: and the one or more liquid reservoirs are provided with three air inlet channels which are respectively communicated with the air suction ports of the three cylinders.
Preferably, in the above three-cylinder rolling rotor compressor, the three cylinders include a first cylinder, a second cylinder and a third cylinder which are sequentially arranged along an axial direction, and the three-cylinder rolling rotor compressor further includes: the upper cylinder cover is arranged above the first cylinder; the first partition plate is arranged between the first cylinder and the second cylinder, and the upper cylinder cover and the first partition plate limit a compression space of the first cylinder; a second partition plate provided between the second cylinder and the third cylinder, the first partition plate and the second partition plate defining a compression space of the second cylinder; and the lower cylinder cover is arranged below the third cylinder, and the second partition plate and the lower cylinder cover limit the compression space of the third cylinder.
Preferably, the three-cylinder rolling rotor compressor further comprises: the upper silencer is arranged above the upper cylinder cover; and the lower silencer is arranged below the lower cylinder cover.
Compared with the prior art, the invention has the beneficial effects that:
the three eccentric parts of the crankshaft are sequentially arranged with a phase difference of 120 degrees, so that when a first piston center point rotates by an angle theta, a second piston center point rotates by an angle theta +120 degrees, and a third piston center point rotates by an angle theta +240 degrees; and the air suction ports of the three cylinders are sequentially arranged with a phase difference of 120 degrees, and at any moment, the volumes of the air suction cavities of the three cylinders are kept consistent, and the volumes of the air exhaust cavities are kept consistent and synchronously changed, so that the acting force of the resultant force of the air in the three cylinders on the crankshaft is constantly zero, the air force borne by the crankshaft is effectively reduced, and the bending degree of the crankshaft is reduced. Meanwhile, compared with a structure that the air suction ports of the three cylinders are positioned on the same side of the compressor, the three-cylinder rolling rotor compressor can properly reduce the shaft diameter of the crankshaft and reduce the abrasion of the crankshaft, thereby improving the performance and the reliability of the compressor to a certain extent.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention, as claimed.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and together with the description, serve to explain the principles of the invention. It is obvious that the drawings in the following description are only some embodiments of the invention, and that for a person skilled in the art, other drawings can be derived from them without inventive effort.
Fig. 1 shows a schematic view of a prior art single rotor compressor;
fig. 2 is a schematic view showing a structure of a twin-rotor type compressor in the related art;
fig. 3 is a schematic structural view showing an upper cylinder and a lower cylinder in a dual-rotor compressor in the prior art;
fig. 4 shows a schematic structural view of a three-cylinder rolling rotor compressor in an embodiment of the present invention;
fig. 5 is a schematic structural view showing a crankshaft of a three-cylinder rolling rotor type compressor in the embodiment of the present invention;
FIG. 6 is a schematic top view of the three eccentric portions of the crankshaft of the three-cylinder rolling rotor compressor in the axial direction according to the embodiment of the present invention;
fig. 7 is a schematic structural view showing three cylinders of a three-cylinder rolling rotor type compressor in the embodiment of the present invention;
fig. 8 is a schematic diagram showing a comparison of resultant gas forces on crankshafts of different rotary compressors for a same capacity and crankshaft size according to an embodiment of the present invention.
Detailed Description
Example embodiments will now be described more fully with reference to the accompanying drawings. Example embodiments may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of example embodiments to those skilled in the art. The same reference numerals in the drawings denote the same or similar structures, and thus their repetitive description will be omitted.
Fig. 4 shows a schematic structural view of a three-cylinder rolling rotor compressor in the embodiment. Referring to fig. 4, in some embodiments, the three-cylinder rolling rotor compressor 2 of the present invention comprises:
the crankshaft 21 has a long shaft portion and three eccentric portions sequentially arranged along an axial direction, axes of the three eccentric portions are distributed on a circle using an axis of the crankshaft as a circle center, and an included angle between the axes of two adjacent eccentric portions is 120 degrees. Specifically, refer to the schematic structural diagram of the crankshaft shown in fig. 5 and the schematic top view of the three eccentric portions of the crankshaft shown in fig. 6 along the axial direction. The crankshaft 21 has long axes arranged in order in the axial direction (the three-cylinder rolling rotor type compressor 2 of the present embodiment is a vertical type compressor, and the crankshaft 21 is vertically arranged in the three-cylinder rolling rotor type compressor 2 of the present embodiment, so the axial direction is referred to as a vertical direction; in other embodiments, the axial direction is correspondingly referred to as a horizontal direction when the technical idea of the present invention is applied to a horizontal type compressor)A portion 211 and three eccentric portions 212, in particular a first eccentric portion 2121, a second eccentric portion 2122 and a third eccentric portion 2123, the axis of the first eccentric portion 2121 (fig. 6 shows the axial center O of the first eccentric portion 2121)1) And the axis of the second eccentric portion 2122 (fig. 6 shows the axial center O of the second eccentric portion 21222) And the axis of the third eccentric part 2123 (fig. 6 shows the axial center O of the third eccentric part 21233) Distributed about the axis O of the crankshaft 2121On a circle (shown by a black bold dashed line in fig. 6) as a center of the circle, and an included angle between the axes of two adjacent eccentric portions is 120 °, that is, the axis O of the first eccentric portion 21211With the axis O of crankshaft 2121Is connected with the axial center O of the second eccentric portion 21222With the axis O of crankshaft 2121Is 120 deg., and the axis O of the second eccentric portion 21222With the axis O of crankshaft 2121Is connected with the axial center O of the third eccentric portion 21233With the axis O of crankshaft 2121The angle between the connecting lines of (a) is 120 deg.. Crankshaft 21 also includes stub shaft portion 213.
The motor assembly 22 is sleeved outside the long shaft portion of the crankshaft 21. The motor assembly may include a rotor sleeved outside the long shaft portion and a stator (not specifically labeled) fixed to an inner wall of the housing 23.
Three pistons are respectively sleeved outside the three eccentric parts of the crankshaft 21. Specifically, the three pistons include a first piston 241, a second piston 242, and a third piston 243, the first piston 241 is sleeved outside the first eccentric portion 2121 of the crankshaft 21, the second piston 242 is sleeved outside the second eccentric portion 2122 of the crankshaft 21, and the third piston 243 is sleeved outside the third eccentric portion 2123 of the crankshaft 21.
And the three cylinders are respectively sleeved outside the three pistons. Specifically, the three cylinders include a first cylinder 251, a second cylinder 252 and a third cylinder 253, the first cylinder 251 is sleeved outside the first piston 241, the second cylinder 252 is sleeved outside the second piston 242, and the third cylinder 253 is sleeved outside the third piston 243.
The side wall of each cylinder is provided with a blade, the blades rotate along with the rotation of the motor assembly 22 driving the crankshaft 21, the crankshaft 21 drives the piston to eccentrically rotate in the cylinder, the blades abut against the piston to divide a compression space between the cylinder and the piston into an air suction cavity and an air exhaust cavity, and the air suction cavity volume and the air exhaust cavity volume of the three cylinders are the same at the same time. When the volumes of the air suction cavities of the three cylinders are the same and the volumes of the air exhaust cavities of the three cylinders are the same, the acting force of the resultant force of the air in the three cylinders on the crankshaft 21 is constant to zero, so that the air force borne by the crankshaft 21 is effectively reduced, and the bending degree of the crankshaft 21 is reduced.
Further, in some embodiments, the three eccentric portions 212 of the crankshaft 21 are sequentially arranged at an angle of 120 ° apart, and the positions of the suction ports of the three cylinders are also sequentially arranged at an angle of 120 ° apart, so that the volumes of the suction chambers of the three cylinders are always kept the same at any time. Referring to the schematic structural diagram of three cylinders of the three-cylinder rolling rotor compressor in the embodiment shown in fig. 7, the side wall of each cylinder is provided with an air suction port and an air discharge port on two sides of the vane, the included angle α between the air suction ports of two adjacent cylinders is equal to 120 °, and the volumes of the compression spaces between each cylinder and the piston are equal. The distance between the vanes and the suction port of each cylinder may be equal or different.
Specifically, referring to fig. 7 (c), the side wall of the first cylinder 251 is provided with an air inlet 2512 and an air outlet 2513 on two sides of a vane 2511 of the first cylinder 251, during the operation of the compressor, the first piston 241 eccentrically rotates in the first cylinder 251, the first vane 2511 abuts against the first piston 241 to divide a crescent-shaped compression space between the first cylinder 251 and the first piston 241 into an air inlet chamber 2514 and an air outlet chamber 2515, the air inlet chamber 2514 sucks air through the air inlet 2512, and the air outlet chamber 2515 exhausts air through the air outlet 2513. Referring to fig. 7 (d), the sidewall of the second cylinder 252 is provided with an air inlet 2522 and an air outlet 2523 on both sides of the vane 2521, during operation of the compressor, the second piston 242 eccentrically rotates in the second cylinder 252, the second vane 2521 abuts against the second piston 242 to divide a crescent-shaped compression space between the second cylinder 252 and the second piston 242 into an air inlet cavity 2524 and an air outlet cavity 2525, the air inlet cavity 2524 sucks air through the air inlet 2522, and the air outlet cavity 2525 exhausts air through the air outlet 2523. Referring to fig. 7 (e), the side wall of the third cylinder 253 is provided with an air inlet 2532 and an air outlet 2533 on two sides of the vane 2531, during operation of the compressor, the third piston 243 eccentrically rotates in the third cylinder 253, the third vane 2531 abuts against the third piston 243 to divide a crescent-shaped compression space between the third cylinder 252 and the third piston 242 into an air inlet cavity 2534 and an air outlet cavity 2535, the air inlet cavity 2534 sucks air through the air inlet 2532, and the air outlet cavity 2535 exhausts air through the air outlet 2533.
As shown in fig. 6 and 7 in conjunction, since the three eccentric portions 212 of the crankshaft 21 are sequentially arranged with a phase difference of 120 °, when the center point of the first piston 241 is rotated by an angle θ in the first cylinder 251, the center point of the second piston 242 is rotated by an angle θ +120 ° in the second cylinder 252, and the center point of the third piston 243 is rotated by an angle θ +240 ° in the third cylinder 253; and because the air suction ports of the three cylinders are also arranged by 120 degrees in sequence, and the volumes of the compression spaces of the three cylinders are equal, the volumes of the air suction cavities of the three cylinders are equal and synchronously changed, and the volumes of the air exhaust cavities of the three cylinders are equal and synchronously changed at any time when the compressor runs. Therefore, the acting force of the resultant force of the gases in the three cylinders on the crankshaft 21 is constantly zero, the gas force borne by the crankshaft 21 is effectively reduced, and the bending degree of the crankshaft 21 is reduced. Meanwhile, compared with a structure that the air suction ports of the three cylinders are positioned on the same side of the compressor, the three-cylinder rolling rotor compressor of the embodiment can properly reduce the shaft diameter of the crankshaft 21 and reduce the abrasion of the crankshaft 21, thereby improving the performance and reliability of the compressor to a certain extent.
Further, the volume of the compression space between each cylinder and the piston can be made equal by the size of the three cylinders being equal and the size of the three pistons being equal. More preferably, the distance between two adjacent eccentric portions of the crankshaft 21 in the axial direction is equal, so as to further improve the stability of the compressor.
In other embodiments, the included angle α between the air inlets of two adjacent cylinders may be between 5 ° and 120 °, and the closer the included angle α is to 120 °, the closer the resultant gas force of the three cylinders is to 0. At this time, although the volumes of the intake chambers and the exhaust chambers of the three cylinders cannot be constantly kept the same, the effect of reducing the resultant force of the gases of the three cylinders applied to the crankshaft 21 can be achieved. When the included angle alpha between the air suction ports of two adjacent cylinders is equal to 120 degrees, the three-cylinder rolling rotor compressor can realize optimal stability, the volumes of the air suction cavities of the three cylinders are completely kept consistent and synchronously changed at any moment, the acting force of the resultant force of the air in the three cylinders on the crankshaft 21 is constantly zero, the air force borne by the crankshaft 21 is reduced to the maximum extent, and the bending degree of the crankshaft 21 is reduced.
Further, the three-cylinder rolling rotor compressor of the present invention further comprises: one or more reservoirs (two reservoirs, a first reservoir 261 and a second reservoir 262, respectively, are shown in fig. 4) have three air-intake channels (a first air-intake channel 2611, a second air-intake channel 2621 and a third air-intake channel 2622, respectively) that communicate with the air-intake ports of the three cylinders, respectively. In other embodiments, three air inlet channels may be provided in the same reservoir, or in three reservoirs. An upper cylinder cover 271 arranged above the first cylinder 251; and a first partition 272 provided between the first cylinder 251 and the second cylinder 252, the upper cylinder cover 271 and the first partition 272 defining a compression space of the first cylinder 251. And a second barrier 273 provided between the second cylinder 252 and the third cylinder 253, the first barrier 272 and the second barrier 273 defining a compression space of the second cylinder 252. And a lower cylinder head 274 provided below the third cylinder 253, the second partition 273 and the lower cylinder head 274 defining a compression space of the third cylinder 253. An upper muffler 281 arranged above the upper cylinder head 271; and a lower muffler 282 provided below the lower cylinder head 274.
The three eccentric parts (namely the first eccentric part 2121, the second eccentric part 2122 and the third eccentric part 2123) of the crankshaft 21 are sequentially arranged in a phase difference of 120 degrees, so that the rotation angles of the central points of the three pistons are sequentially arranged in a phase difference of 120 degrees, namely when the central point of the first piston 241 rotates by an angle theta, the central point of the second piston 242 rotates by an angle theta +120 degrees, the central point of the third piston 243 rotates by an angle theta +240 degrees, the air suction ports of the three cylinders (namely the first cylinder 251, the second cylinder 252 and the third cylinder 253) are also sequentially arranged in a phase difference of 120 degrees, and the volumes of compression spaces between each cylinder and the pistons are the same, so that the volumes of air suction cavities of the three cylinders are kept consistent and the volumes of exhaust cavities are kept consistent and synchronously changed at any time of the operation of the compressor, and the acting force of the air in the three cylinders on the crankshaft 21 is constantly kept to be zero.
Referring to fig. 8, a schematic diagram of the resultant gas forces on the crankshafts of different rotary compressors under the same capacity and crankshaft size in the embodiment is shown. The abscissa is the crankshaft angle in degrees, and the ordinate is the resultant force of the gases on the crankshaft in N. Curve 31 represents the resultant gas force on the crankshaft in the conventional single-rotor compressor, curve 32 represents the resultant gas force on the crankshaft in the conventional dual-rotor compressor (the suction ports of the two cylinders are located on the same side), curve 33 represents the resultant gas force on the crankshaft in the conventional three-rotor compressor (the suction ports of the three cylinders are located on the same side), and curve 34 represents the resultant gas force on the crankshaft in the three-cylinder rolling rotor compressor (the suction ports of the three cylinders are arranged in a staggered manner, the included angle α between the suction ports of the two adjacent cylinders is between 5 ° and 120 °, and in the preferred embodiment, the included angle α is equal to 120 °). It can be seen that, with the three-cylinder rolling rotor compressor structure of the present invention, the acting force of the resultant force of the gas in the three cylinders on the crankshaft is constantly zero, so that the gas force borne by the crankshaft can be effectively reduced, and the bending degree of the crankshaft can be reduced. Meanwhile, compared with a structure that the air suction ports of the three cylinders are positioned on the same side of the compressor, the three-cylinder rolling rotor compressor can properly reduce the shaft diameter of the crankshaft and reduce the abrasion of the crankshaft, thereby improving the performance and the reliability of the compressor to a certain extent.
The foregoing is a more detailed description of the invention in connection with specific preferred embodiments and it is not intended that the invention be limited to these specific details. For those skilled in the art to which the invention pertains, several simple deductions or substitutions can be made without departing from the spirit of the invention, and all shall be considered as belonging to the protection scope of the invention.
Claims (8)
1. A three-cylinder rolling rotor compressor, comprising:
the crankshaft is provided with a long shaft part and three eccentric parts which are sequentially arranged along the axial direction, the axes of the three eccentric parts are distributed on a circle which takes the axis of the crankshaft as the circle center, and the included angle between the axes of two adjacent eccentric parts is 120 degrees;
the motor assembly is sleeved outside the long shaft part;
the three pistons are respectively sleeved outside the three eccentric parts; and
the three cylinders are respectively sleeved outside the three pistons;
the side wall of each cylinder is provided with a blade, the crankshaft is driven to rotate along with the motor assembly, the crankshaft drives the piston to eccentrically rotate in the cylinder, the blade abuts against the piston to divide a compression space between the cylinder and the piston into an air suction cavity and an air exhaust cavity, and the air suction cavities of the three cylinders have the same volume and the same volume.
2. A three-cylinder rolling rotor compressor according to claim 1, wherein the side wall of each cylinder is provided with an air suction port and an air discharge port at both sides of the vane thereof, respectively, and the angle α between the air suction ports of two adjacent cylinders satisfies: alpha is more than or equal to 5 degrees and less than or equal to 120 degrees.
3. A three-cylinder rolling rotor compressor according to claim 2, characterized in that said included angle α is equal to 120 ° and the volume of the compression space of each of said cylinders is equal.
4. A three-cylinder rolling rotor compressor as claimed in claim 3 wherein the three cylinders are of equal size and the three pistons are of equal size.
5. A three-cylinder rolling rotor compressor according to claim 1, wherein the distances in the axial direction between the adjacent eccentric portions are equal.
6. A three-cylinder rolling rotor compressor according to claim 1, further comprising:
and the one or more liquid reservoirs are provided with three air inlet channels which are respectively communicated with the air suction ports of the three cylinders.
7. A three-cylinder rolling rotor compressor according to claim 1, wherein the three cylinders include a first cylinder, a second cylinder and a third cylinder which are arranged in order in the axial direction, the three-cylinder rolling rotor compressor further comprising:
the upper cylinder cover is arranged above the first cylinder;
the first partition plate is arranged between the first cylinder and the second cylinder, and the upper cylinder cover and the first partition plate limit a compression space of the first cylinder;
a second partition plate provided between the second cylinder and the third cylinder, the first partition plate and the second partition plate defining a compression space of the second cylinder; and
and the lower cylinder cover is arranged below the third cylinder, and the second partition plate and the lower cylinder cover limit the compression space of the third cylinder.
8. A three-cylinder rolling rotor compressor according to claim 7, further comprising:
the upper silencer is arranged above the upper cylinder cover; and
and the lower silencer is arranged below the lower cylinder cover.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910483111.5A CN112032052B (en) | 2019-06-04 | 2019-06-04 | Three-cylinder rolling rotor compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910483111.5A CN112032052B (en) | 2019-06-04 | 2019-06-04 | Three-cylinder rolling rotor compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112032052A true CN112032052A (en) | 2020-12-04 |
| CN112032052B CN112032052B (en) | 2022-10-04 |
Family
ID=73576446
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910483111.5A Active CN112032052B (en) | 2019-06-04 | 2019-06-04 | Three-cylinder rolling rotor compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112032052B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102022116197A1 (en) | 2022-06-29 | 2024-01-04 | Schaeffler Technologies AG & Co. KG | Orbital piston compressor with circumferentially offset cylinder assemblies and shaft-integrated bearing seats |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1900541A (en) * | 2005-07-21 | 2007-01-24 | 李玉斌 | Crankshaft for three cylinder rotary compressor |
| CN103807174A (en) * | 2014-03-10 | 2014-05-21 | 吴月广 | Three-cylindrical rolling rotor type compressor |
| US20160018136A1 (en) * | 2013-03-26 | 2016-01-21 | Toshiba Carrier Corporation | Multiple cylinder rotary compressor and refrigeration cycle apparatus |
| CN208221100U (en) * | 2018-05-30 | 2018-12-11 | 广东美芝制冷设备有限公司 | Multi-cylinder rotation compressor |
| CN208487015U (en) * | 2018-07-25 | 2019-02-12 | 广东美芝精密制造有限公司 | The compression mechanism and rotary compressor of rotary compressor |
-
2019
- 2019-06-04 CN CN201910483111.5A patent/CN112032052B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1900541A (en) * | 2005-07-21 | 2007-01-24 | 李玉斌 | Crankshaft for three cylinder rotary compressor |
| US20160018136A1 (en) * | 2013-03-26 | 2016-01-21 | Toshiba Carrier Corporation | Multiple cylinder rotary compressor and refrigeration cycle apparatus |
| CN103807174A (en) * | 2014-03-10 | 2014-05-21 | 吴月广 | Three-cylindrical rolling rotor type compressor |
| CN208221100U (en) * | 2018-05-30 | 2018-12-11 | 广东美芝制冷设备有限公司 | Multi-cylinder rotation compressor |
| CN208487015U (en) * | 2018-07-25 | 2019-02-12 | 广东美芝精密制造有限公司 | The compression mechanism and rotary compressor of rotary compressor |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102022116197A1 (en) | 2022-06-29 | 2024-01-04 | Schaeffler Technologies AG & Co. KG | Orbital piston compressor with circumferentially offset cylinder assemblies and shaft-integrated bearing seats |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112032052B (en) | 2022-10-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN112032051B (en) | Four-cylinder rolling rotor type compressor | |
| CN101709701B (en) | Single-cylinder multistage gas-compression rolling piston compressor | |
| CN112032052B (en) | Three-cylinder rolling rotor compressor | |
| CN102410221B (en) | Double-cylinder rotary compressor | |
| JP2003227485A (en) | Multi-cylinder compressors | |
| EP4170174A1 (en) | Rotary compressor | |
| CN215292888U (en) | Rotary compressor | |
| EP3933168A1 (en) | Rotary compressor | |
| JP6257806B2 (en) | Multi-cylinder hermetic compressor | |
| KR101418288B1 (en) | Hermetic compressor | |
| CN114688026A (en) | Multi-cylinder rotary compressor | |
| CN112879283A (en) | Triangular rotor pump | |
| CN113700648A (en) | Rotary compressor | |
| CN214403981U (en) | Multi-cylinder rotary compressor | |
| CN214424691U (en) | Triangular rotor pump | |
| EP4151833A1 (en) | Rotary compressor | |
| JP2673431B2 (en) | Gas compressor | |
| CN107120275B (en) | Compression mechanism and rotary compressor | |
| KR100324770B1 (en) | Stroke volume magnification structure for enclosed compressor | |
| JP2937895B2 (en) | Rotary compressor | |
| RU65976U1 (en) | ROTARY-VAN ENGINE-PUMP | |
| JPH0138313Y2 (en) | ||
| JP2005226607A (en) | Vane pump | |
| KR100336135B1 (en) | Cylinder design for rotary compressor | |
| KR20230066964A (en) | Vane rotary compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |