CN106837790B - Rotary compressor, refrigerating system and temperature adjusting equipment - Google Patents

Rotary compressor, refrigerating system and temperature adjusting equipment Download PDF

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Publication number
CN106837790B
CN106837790B CN201710008622.2A CN201710008622A CN106837790B CN 106837790 B CN106837790 B CN 106837790B CN 201710008622 A CN201710008622 A CN 201710008622A CN 106837790 B CN106837790 B CN 106837790B
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China
Prior art keywords
cylinder
air suction
sliding
partition plate
disc
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CN201710008622.2A
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Chinese (zh)
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CN106837790A (en
Inventor
阙沛祯
魏会军
杨欧翔
胡艳军
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Priority to CN201710008622.2A priority Critical patent/CN106837790B/en
Publication of CN106837790A publication Critical patent/CN106837790A/en
Priority to PCT/CN2017/106287 priority patent/WO2018126758A1/en
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    • 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • F04C2240/00—Components
    • F04C2240/10—Stators
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Abstract

The invention relates to a rotary compressor, at least having a multi-sliding-vane cylinder, the multi-sliding-vane cylinder comprising: a cylinder body; a plurality of sliding vanes disposed within the cylinder body; the crankshaft and a rotor which is arranged on the crankshaft and matched with the sliding sheet; the disc partition board is fixedly connected to the crankshaft and used for sealing the bottom end or the top end of the cylinder body; the air suction notch is formed in the excircle of the disc partition plate, and is communicated with the working cavity when the volume of the working cavity in the cylinder body is increased; when the volume of the working chamber is reduced, the disc partition plate closes the working chamber. The rotary compressor can effectively prevent the phenomenon of air suction countercurrent in the multi-sliding-vane cylinder, ensures that all gas sucked into the multi-sliding-vane cylinder is compressed, and effectively expands the discharge capacity of the rotary compressor. The invention also relates to a refrigerating system adopting the rotary compressor and a temperature regulating device adopting the refrigerating system.

Description

Rotary compressor, refrigerating system and temperature adjusting equipment
Technical Field
The invention relates to the technical field of compressor manufacturing, in particular to a rotary compressor, a refrigerating system and temperature regulating equipment.
Background
In order to enlarge the displacement of the current single-cylinder rotor compressor and reduce the vibration of the single-cylinder compressor, the compressor in the prior art generally adopts a double-cylinder structure, the double-cylinder structure is that two superposed cylinders are arranged in the axial direction of the compressor, and a partition plate is used for separating the two cylinders.
However, the double-cylinder structure has two cylinders, the height direction is large in size, the bearing span is large, the bearing reliability is poor, and meanwhile, compared with a single-cylinder structure, one cylinder compression assembly is added, two air suction ports are needed, the overall cost of the compressor is high, and in addition, the compressor also has the problems of leakage and large friction force.
In order to overcome the above-mentioned disadvantages of the double-cylinder compressor, those skilled in the art have provided two sliding vanes on the cylinder body of the single-cylinder compressor, and one sliding vane is used for one cylinder, so as to achieve the purpose of two working chambers in one cylinder, so as to reduce the vibration of the compressor and make the structure thereof compact while expanding the displacement of the compressor.
The compressor of single cylinder double-sliding-piece structure has two induction ports, this leads to the gas that has inhaled in the cylinder to discharge from the induction port again (inhale the problem of flow against the contrary) easily, this makes the actual discharge capacity of compressor increase very limitedly, in order to solve the problem of inhaling the flow against the current, a mode of setting up the stop valve on the induction port has appeared, nevertheless can show the inspiratory resistance that increases the compressor behind the increase stop valve, lead to the consumption of compressor to increase, still can have the clearance volume between stop valve and the induction port simultaneously, can't really solve the problem of inhaling the flow against the current completely.
Therefore, how to prevent the phenomenon of reverse flow of suction gas when a plurality of sliding vanes are arranged in one cylinder so as to effectively expand the displacement of the compressor is a technical problem which needs to be solved by those skilled in the art.
Disclosure of Invention
One of the objectives of the present invention is to provide a rotary compressor, so as to prevent the suction backflow phenomenon of the multi-sliding-vane cylinder, effectively expand the displacement of the multi-sliding-vane cylinder, and improve the energy efficiency of the compressor.
Another object of the present invention is to provide a refrigeration system using the above rotary compressor.
Still another object of the present invention is to provide a temperature adjusting device using the above refrigeration system.
To achieve the above object, the present invention provides a rotary compressor having at least one multiple sliding vane cylinder, the multiple sliding vane cylinder including:
a cylinder body;
a plurality of sliding vanes disposed within the cylinder body;
the crankshaft and a rotor are arranged on the crankshaft and matched with the sliding sheet;
the disc partition plate is fixedly connected to the crankshaft and used for sealing the bottom end or the top end of the cylinder body;
the air suction notch is formed in the excircle of the disc partition plate, and is communicated with the working cavity when the volume of the working cavity in the cylinder body is increased; when the volume of the working chamber is reduced, the disc partition plate seals the working chamber.
Preferably, the multiple-vane cylinder further includes:
the disc partition plate is provided with an air suction part provided with an air suction port, a cavity is arranged inside the air suction part, and the inner wall of the cavity is matched with the outer circle of the disc partition plate to form an air suction cavity communicated with the air suction port.
Preferably, the multi-vane rotary compressor is a single cylinder compressor.
Preferably, two sliding sheets are arranged in the cylinder body.
Preferably, the included angle between the two sliding pieces is 90-270 degrees.
Preferably, the breach of breathing in is fan-shaped, just the outer arc of the breach of breathing in does the excircle of disc baffle, the inner arc of the breach of breathing in with the eccentric part of bent axle is concentric, the central angle that the breach of breathing in corresponds is less than two minimum contained angle between the gleitbretter.
Preferably, the included angle between the two sliding pieces is 180 degrees.
Preferably, the air suction gap is fan-shaped, an outer arc of the air suction gap is an outer circle of the disc partition plate, an inner arc of the air suction gap is concentric with an eccentric part of the crankshaft, and the rotation direction of the crankshaft is reversed by theta with an eccentric tangent point of the crankshaft as a starting point1Starting from the eccentric tangent point of the crankshaft, the intake notch is rotated by θ in the reverse direction to the rotation direction of the crankshaft2As a dead point of the air intake gap, wherein 0 DEG < theta1＜45°，50°＜θ2＜110°。
Preferably, the radius of the inner arc of the air suction notch is R1The radius of the disc partition plate is R2And 0.8 < R1/R2＜1。
Preferably, the air suction piece is a lower flange of the compressor, and the disc partition plate seals the bottom end of the cylinder body.
Preferably, the upper end surface of the lower flange of the compressor and the cylinderA partition plate with a middle through hole is further arranged between the bottom ends of the body, the disc partition plate is embedded in the middle through hole, and the radius of the disc partition plate is R2The radius of the middle through hole of the partition plate is R5Wherein R is5-R2≥0.01mm。
Preferably, the thickness of the disc separator is H1The thickness of the separating plate is H2And H is2-H1≥0.01mm。
Preferably, the radius of the disc partition is R2The inner diameter of the cylinder body is R3And 1.1 < R2/R3＜1.5。
Preferably, the rotary compressor comprises two multi-sliding-vane cylinders, the two multi-sliding-vane cylinders are respectively a first cylinder and a second cylinder which are axially arranged along the compressor, the disc partition plate is a first disc partition plate and a second disc partition plate which are arranged at intervals, the first disc partition plate is used for sealing the bottom end of the first cylinder, the second disc partition plate is used for sealing the top end of the second cylinder, the air suction notch is a first air suction notch arranged on the first disc partition plate and a second air suction notch arranged on the second disc partition plate, and the air suction piece is arranged between the first cylinder and the second cylinder and sleeves the first disc partition plate and the second disc partition plate into a partition plate in the cavity of the rotary compressor.
Preferably, the first air suction notch and the second air suction notch are staggered with each other.
Preferably, the included angle between the first air suction notch and the second air suction notch is 90 degrees.
Preferably, two sliding sheets are arranged in any one cylinder.
Preferably, the rotary compressor includes one multi-sliding-vane cylinder and one single-sliding-vane cylinder, and an exhaust port of the multi-sliding-vane cylinder is communicated with an intake port of the single-sliding-vane cylinder.
Preferably, the rotary compressor includes one multi-sliding-vane cylinder and one single-sliding-vane cylinder, and an air suction port of the multi-sliding-vane cylinder is communicated with an air discharge port of the single-sliding-vane cylinder.
Preferably, the cylinder body of the multi-sliding-vane cylinder is internally provided with three sliding vanes which are uniformly distributed along the circumferential direction of the cylinder body.
The refrigeration system disclosed by the invention comprises a compressor, a condenser, a throttling device and an evaporator, wherein the compressor is a rotary compressor disclosed in any one of the above.
The temperature adjusting device disclosed by the invention is provided with a refrigerating system, and the refrigerating system is the refrigerating system.
Preferably, the temperature adjusting device is an air conditioner or a refrigerator.
The rotary compressor disclosed by the invention is at least provided with one multi-sliding-vane cylinder, wherein the multi-sliding-vane cylinder comprises basic components such as a cylinder body, sliding vanes, a crankshaft and the like, but an air suction port is not arranged on the cylinder body, a disc partition plate is fixedly arranged on the crankshaft and synchronously rotates along with the crankshaft, the disc partition plate is used for sealing the bottom end or the top end of the cylinder body, an air suction notch is formed in the disc, and in the process of rotating along with the crankshaft, when the volume of a working cavity formed by a rotor, the cylinder body and the sliding vanes is increased, the air suction notch is communicated with the increased working cavity to realize air suction; when the volume of working chamber reduces, the breach of breathing in is isolated with the working chamber that is reducing, and the disc baffle will seal the working chamber that is reducing, avoids gaseous not compressing and discharges again. Therefore, the rotary compressor disclosed by the invention can effectively prevent the phenomenon of reverse suction flow in the multi-sliding-vane cylinder, ensures that all gas sucked into the multi-sliding-vane cylinder is compressed, effectively expands the discharge capacity of the rotary compressor, and has the advantages of no stop valve, small suction resistance, low energy consumption, stable operation of the multi-sliding-vane cylinder, small vibration and high energy efficiency.
Drawings
Fig. 1 is a schematic structural view of a rotary compressor disclosed in a first embodiment of the present invention;
FIG. 2 is an enlarged view of a portion H of FIG. 1;
fig. 3 is an exploded schematic view of a rotary compressor disclosed in a first embodiment of the present invention;
FIG. 4 is a schematic illustration of the crankshaft of FIG. 3;
FIG. 5 is a schematic top view of the upper flange of FIG. 4;
FIG. 6 is a schematic view of the divider plate of FIG. 4;
FIG. 7 is a schematic structural view of the lower flange of FIG. 4;
FIG. 8 is a schematic view of the cylinder of FIG. 4;
FIG. 9 is a schematic view showing the fitting relationship of the parts of the cylinder in the first embodiment of the present invention;
FIG. 10 is a schematic view showing the structure of the rotor rotated by 45 ° in the first embodiment of the present invention;
FIG. 11 is a schematic view showing the structure of the rotor rotated by 90 ° in the first embodiment of the present invention;
FIG. 12 is a schematic view showing the structure of the rotor rotating 135 ° according to the first embodiment of the present invention;
FIG. 13 is a schematic view showing the structure of the rotor rotated 180 degrees in the first embodiment of the present invention;
FIG. 14 is a schematic view showing the structure of the rotor rotated by 225 deg. in the first embodiment of the present invention;
FIG. 15 is a schematic structural view of the rotor rotating 270 in the first embodiment of the present invention;
FIG. 16 is a schematic view showing the structure of the rotor rotated 315 ° in the first embodiment of the present invention;
FIG. 17 is a schematic view showing a structure of a rotor rotating 360 degrees according to the first embodiment of the present invention;
fig. 18 is a schematic structural view of a rotary compressor disclosed in a second embodiment of the present invention;
FIG. 19 is a schematic illustration of the crankshaft of FIG. 18;
FIG. 20 is a schematic view showing the structure of the partition plate of FIG. 18;
fig. 21 is a schematic structural view of a rotary compressor disclosed in a third embodiment of the present invention;
fig. 22 is a schematic structural view of a rotary compressor disclosed in a fourth embodiment of the present invention;
fig. 23 is a schematic structural view of the refrigeration system disclosed in the embodiment of the present invention.
The compressor comprises a crankshaft 1, an eccentric part 2, a rotor 3, an upper flange 4, a cylinder body 5, a separation plate 6, a lower flange 7, a cavity 8, a disc separation plate 9, an exhaust port 10, a sliding vane 11, an air suction port 12, an air suction notch 13, a middle through hole 14, a sliding vane groove 15, an exhaust notch 16, a first disc separation plate 17, a second disc separation plate 18, an upper sealing plate 19, a separation plate 20, a high-pressure cylinder 21, a condenser 22, a throttling device 23, an evaporator 24 and a gas-liquid separator 25.
Detailed Description
The core of the invention is to provide a rotary compressor, so as to prevent the phenomenon of reverse suction flow of a multi-sliding-vane cylinder, effectively expand the displacement of the multi-sliding-vane cylinder and improve the energy efficiency of the compressor.
Another core of the present invention is to provide a refrigerating system using the above rotary compressor.
The invention further provides a temperature adjusting device adopting the refrigerating system.
In order that those skilled in the art will better understand the disclosure, the invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
The rotary compressor disclosed by the invention at least comprises a multi-sliding-vane cylinder, wherein the multi-sliding-vane cylinder is a cylinder in which a plurality of sliding vanes are arranged, and the multi-sliding-vane cylinder specifically comprises: the compressor comprises a cylinder body 5, a sliding sheet 11, a crankshaft 1 and a disc partition board 9, wherein the sliding sheet 11 is arranged in the cylinder body 5, the crankshaft 1 penetrates through the cylinder body 5, the crankshaft 1 is provided with a rotor 3 which is used for being matched with the sliding sheet 11 to form a working cavity, the disc partition board 9 is fixedly arranged on the crankshaft 1, the disc partition board 9 is used for sealing the bottom end or the top end of the cylinder body 5, it can be easily understood that when the disc partition board 9 seals the bottom end of the cylinder body 5, the disc partition board 9, the sliding sheet 11, the rotor 3 and an upper flange 4 of a cylinder jointly enclose the working cavity of the compressor, as the sliding sheet 11 comprises a plurality of sliding sheets, the cylinder body 5 is divided into a plurality of independent and periodically-changed working cavities, an air suction notch 13 is arranged on the excircle of the disc partition board 9, and when the volume of the working cavity in the, the air suction gap 13 is communicated with the working cavity; when the volume of the working chamber is reduced, the disc partition 9 closes the working chamber.
The disc partition plate 9 rotates along with the crankshaft 1, and when the volume of a working cavity formed by the rotor 3, the cylinder body 5 and the sliding sheet 11 is increased, the air suction notch 13 is communicated with the increased working cavity to realize air suction; when the volume of the working chamber is reduced, the air suction gap 13 is isolated from the reducing working chamber, and the disc partition plate 9 seals the reducing working chamber to prevent the gas from being discharged again without compression. Therefore, the rotary compressor disclosed by the invention can effectively prevent the phenomenon of reverse suction flow in the multi-sliding-vane cylinder, ensures that all gas sucked into the multi-sliding-vane cylinder is compressed, effectively expands the discharge capacity of the rotary compressor, and has the advantages of no stop valve, small suction resistance, low energy consumption, stable operation of the multi-sliding-vane cylinder, small vibration and high energy efficiency.
It is easily understood by those skilled in the art that the exhaust notch on the cylinder body 5 should be arranged next to the sliding vane slot 15, the arrangement position of the exhaust port 10 of the compressor is not limited, for the convenience of installation of the compressor, the exhaust port 10 of the compressor is usually arranged on the upper flange 4 or the lower flange 7, in order to further optimize the above technical solution, the multi-sliding vane cylinder further comprises a suction member, the suction member is provided with an air suction port 12, the inside of the suction member 12 is provided with a cavity 8, and the inner wall of the cavity 8 is used for cooperating with the outer circle of the disc partition 9 to form a suction cavity communicated with the air suction port 12.
In the following, the invention will be described in detail in the context of a number of different embodiments.
First embodiment
Referring to fig. 1 to 17, the rotary compressor disclosed in this embodiment is a single-cylinder rotary compressor, which includes an upper flange 4, a cylinder body 5, a crankshaft 1, and a lower flange 7, in this embodiment, the lower flange 7 is used as a suction member, accordingly, a disc partition 9 is used to close the bottom end of the cylinder body 5, and the top end of the cylinder body 5 is closed by the upper flange 4, as shown in fig. 1, the number of sliding pieces 11 disposed in the cylinder body 5 is practically unlimited, for example, may be 2, 3 or more, in this embodiment, 2 sliding pieces 11 are taken as an example, an included angle between two sliding pieces 11 is preferably 90 ° to 270 ° so as to divide the interior of the cylinder body 5 into two larger cavities, in this embodiment, the included angle between two sliding pieces 11 is 180 °, in this embodiment, the shape of the suction gap 13 is a sector, as shown in fig. 3, 4 and 9, the outer arc of the air suction gap 13 is the outer circle of the disc partition 9, the inner arc of the air suction gap 13 is concentric with the eccentric portion 2 of the crankshaft 1, and the central angle corresponding to the air suction gap 13 is smaller than the minimum included angle between the two sliding pieces 11, so as to ensure that the air can be compressed in each cavity.
As shown in fig. 8, the cylinder body 5 in this embodiment has two opposite sliding sheet slots 15 therein, and exhaust slits 16 are respectively provided at one side of the sliding sheet slot 15, and no intake port is provided on the cylinder, as shown in fig. 4, the crankshaft 1 includes a long axis, a short axis and an eccentric portion 2, one side of the eccentric portion 2 is provided with a disc partition plate 9 integrally connected with the crankshaft 1, an intake notch 13 is provided on the disc partition plate 9, the disc partition plate 9 and the intake notch 13 rotate synchronously with the crankshaft 1, the disc partition plate 9 functions to seal the lower end surface of the cylinder body 5, and the intake notch 13 can communicate a working chamber whose volume is increasing with the intake port 12, and an exhaust port 10 communicating with the exhaust slit 16 provided on the cylinder is provided on the upper flange 4, as shown in fig. 5, the exhaust port 10 specifically includes two, and respectively communicating with the two exhaust slits 16 on the cylinder, as shown in fig. 7, the lower flange 7 is provided with a bearing hole for mounting the short shaft of the crankshaft 1, the lower flange 7 is provided with a cavity 8 therein, the side wall of the lower flange 7 is provided with an air suction port 12 communicated with the cavity 8, since the upper end of the bearing hole is flush with the upper end surface of the lower flange 7, in order to ensure that the disc partition plate 9 can rotate smoothly, the embodiment is additionally provided with the partition plate 6, as shown in fig. 6, the partition plate 6 is provided with a middle through hole 14, and the radius of the middle through hole 14 is R5The radius of the disc partition is R2，R5-R2Not less than 0.01mm, the thickness of the disc partition plate 9 is H1Thickness of the partition plate 6Degree of H2And H is2-H1Not less than 0.01mm to ensure that the partition plate 6 can provide enough rotating space for the disc partition plate 9.
Referring to fig. 3, the assembly of the components is shown in the figure, the short shaft of the crankshaft 1 is installed in the bearing hole of the lower flange 7, the lower end face of the disc partition 9 is placed in the cavity 8 of the lower flange 7, and the excircle of the disc clapboard 9 is matched with the inner wall of the cavity 8 of the lower flange 7 to enclose a gas suction cavity, the disc clapboard 9 is sleeved in a middle through hole 14 of the clapboard 6, the clapboard 6 is placed on the upper end surface of the lower flange 7, the cylinder body 5 is arranged on the upper end surface of the clapboard 6, meanwhile, the rotor 3 is arranged in the cylinder and sleeved outside the eccentric part 2 of the crankshaft 1, the sliding sheets 11 are respectively placed in the two sliding sheet grooves 15, the upper flange 4 is finally arranged, the inner hole of the upper flange 4 is sleeved on the long shaft of the crankshaft 1, the lower end face of the upper flange 4 is placed on the upper end face of the cylinder body 5, and the two exhaust ports 10 of the upper flange 4 are respectively covered at the exhaust notches 16 of the cylinder.
In order to ensure the sealing of the working chamber and the smooth operation of the crankshaft, in the embodiment, the outer diameter of the disc partition plate 9 is R2, the inner diameter of the cylinder body 5 is R3, and 1.1 < R2/R3 < 1.5, that is, the diameter of the disc partition plate 9 is larger than the inner diameter of the cylinder body 5, so that the plate surface of the disc partition plate 9 is in sealing fit with the lower end surface of the cylinder body 5, as shown in fig. 9, the arrow in fig. 9 represents the rotation direction of the crankshaft, in order to optimize the suction of the working chamber, the suction gap 13 formed on the disc partition plate 9 of the crankshaft 1 is in a fan shape, the outer arc of the suction gap 13 is the outer circle of the disc partition plate 9, the inner arc of the suction gap 13 is concentric with the eccentric portion of the crankshaft 1, the eccentric tangent point of the crankshaft 1 is taken as the starting point, the reverse rotation direction θ 1 of the crankshaft 1 is taken as the starting point of the, the rotation θ 2 in the reverse direction of the rotation of the crankshaft 1 is defined as the dead point of the air intake gap 13, where 0 ° < θ 1 < 45 °, 50 ° < θ 2 < 110 °, the radius of the inner arc of the air intake gap 13 is R1, the radius of the disc partition 9 is R2, and 0.8 < R1/R2 < 1, and it should be noted that the eccentric tangent point of the crankshaft 1 in the present embodiment is defined as the point on the eccentric portion 2 of the crankshaft 1 at which the distance from the rotation center of the crankshaft is the largest.
According to the assembly relation among the parts, the cylinder body 5, the upper flange 4, the disc partition plate 9, the rotor 3 and the sliding piece 11 form working chambers in the cylinder, as shown in fig. 10 to 17, the working chambers include 3 working chambers, namely a working chamber i, a working chamber ii and a working chamber iii, and the air suction notch 13 on the disc partition plate 9 rotates along with the crankshaft 1, so that the three working chambers are continuously and alternately changed from air suction, compression to air exhaust.
Fig. 10 to 17 show the variation process of each working chamber in the range of 45 ° to 360 ° of crankshaft rotation with the slide 11 located at the top in the drawing as the starting point of 0 ° of the crankshaft.
In fig. 10, when the crankshaft rotates by 45 °, the volume of the working chamber i is continuously increased, the working chamber i is communicated with the air suction chamber of the lower flange 7 through the air suction gap 13 formed in the disc partition plate 9, and air suction is performed through the air suction gap 13; the working cavity II is closed by the disc partition plate 9, the volume is continuously reduced, the compression process is carried out, and high-pressure refrigerant is discharged through an exhaust notch 16 on the cylinder; the volume of the working cavity III is also increased at the moment, the working cavity III is also communicated with the air suction cavity of the lower flange 7 through an air suction gap 13 formed in the disc partition plate 9, and air suction is carried out through the air suction gap 13;
in fig. 11, when the crankshaft rotates 90 °, the volume of the working chamber i is continuously increased, the working chamber i is communicated with the air suction chamber of the lower flange 7 through the air suction gap 13 formed in the disc partition plate 9, and air suction is performed through the air suction gap 13; the working cavity II is closed by the disc partition plate 9, the volume is continuously reduced, the compression process is carried out, and high-pressure refrigerant is discharged through an exhaust notch 16 on the cylinder; the volume of the working chamber III reaches the maximum at this time, the disc partition plate 9 closes the working chamber III and is in a critical state of air suction ending and compression starting;
in fig. 12, when the crankshaft rotates 135 °, the volume of the working chamber i is still increasing, the working chamber i is communicated with the air suction chamber of the lower flange 7 through the air suction gap 13 formed in the disc partition 9, and air suction is performed through the air suction gap 13; the working cavity II is closed by the disc partition plate 9, the volume is still continuously reduced, compression and exhaust are carried out, and high-pressure refrigerant is discharged through an exhaust notch 16 on the cylinder; the volume of the working chamber III is reduced at the moment, the disc partition plate 9 seals the working chamber III, the compression process is carried out, and when the gas pressure reaches a discharge value, the gas is discharged through a discharge notch 16 on the cylinder;
in fig. 13, when the crankshaft rotates 180 °, the volume of the working chamber i is still increasing, and the working chamber i still inhales through the air intake gap 13; the volume of the working chamber II is reduced to 0, and the exhaust is finished; the volume of the working chamber III is still reduced at the moment, the disc partition plate 9 seals the working chamber III, and the compression and exhaust processes are carried out;
in fig. 14, when the crankshaft rotates 225 °, the volume of the working chamber i is still increasing, and the working chamber i still sucks air through the air suction gap 13; the volume of the working cavity II begins to increase, the working cavity II is communicated with the air suction cavity of the lower flange 7 through an air suction gap 13 formed in the disc partition plate 9, and air suction is carried out through the air suction gap 13; the volume of the working chamber III is still reduced at the moment, the disc partition plate 9 seals the working chamber III, and the compression and exhaust processes are carried out;
in fig. 15, when the crankshaft rotates 270 °, the volume of the working chamber i reaches the maximum, the suction stops, and the disc diaphragm 9 closes it, which is in the critical state of suction ending and compression starting; the volume of the working cavity II is increased, and air suction is carried out through the air suction gap 13; the volume of the working chamber III is still reduced at the moment, the disc partition plate 9 seals the working chamber III, and the compression and exhaust processes are carried out;
in fig. 16, when the crankshaft rotates 315 °, the volume of the working chamber i decreases, closing it by the disc diaphragm 9, and the compression process is in progress; the volume of the working cavity II is increased, and air suction is carried out through the air suction gap 13; the volume of the working chamber III is continuously reduced at the moment, the working chamber III is sealed by the disc partition plate 9, and the exhaust process is carried out;
in fig. 17, when the crankshaft rotates 360 °, the volume of the working chamber i decreases, and the disc partition 9 closes it, and the compression and exhaust process is being performed; the volume of the working cavity II is still increased, and air suction is carried out through the air suction gap 13; the volume of the working chamber III is reduced to 0 at the moment, and the exhaust is finished;
it can be seen from the above working processes that 3 working chambers of the compressor continuously perform the alternate change of air suction, compression and exhaust within the rotation angle range of 360 degrees of crankshaft 1 rotation, for each working chamber, one and a half of crankshaft 1 rotation completes one complete cycle of the compressor, for the whole compressor, each rotation of crankshaft 1 has two exhaust processes, the maximum volume of the working chamber is at 90 degrees and 270 degrees of crankshaft rotation, because there is no air suction port on the cylinder body 5, the air suction of the working chamber is realized through the air suction notch 13 arranged on the disc partition plate 9, the air suction notch 13 rotates with the crankshaft rotation, it can realize that in the process of increasing the volume of a single working chamber, the working chamber can be communicated with the air suction notch 13 for air suction, after the volume of the working chamber reaches the maximum, the working chamber can be separated from the air suction notch 13, there is no gas backflow after the working chamber is compressed, the discharge capacity of the compressor is greatly improved. The effective volume of compressor in this embodiment is the working chamber maximum volume and is in the working chamber volume of crankshaft rotation to 90 and the working chamber when the crankshaft rotates to 270 and compares with traditional with the single sliding vane compressor of size structure, and effective volume can promote 50% -60%.
According to the above working process, when one side of the compressor finishes sucking and starts compressing, and the other side of the compressor finishes exhausting and starts sucking, the working principle makes the compressor have smaller torque fluctuation and bearing load than the traditional single-cylinder single-sliding-vane compressor in the compressing process, so that the vibration of the compressor is smaller than that of the common compressor.
Second embodiment
The basic principle of the present embodiment is the same as that of the first embodiment, and is different from the first embodiment in that the rotary compressor in the present embodiment is a two-cylinder compressor, and the two cylinders are both multi-vane cylinders, and the two multi-vane cylinders are arranged along the axial direction of the compressor, and are respectively a first cylinder and a second cylinder, and correspondingly, the disc partition plate 9 also includes two disc partition plates 17 and 18, which are arranged at intervals, as shown in fig. 18 and 19. The first disc partition plate 17 is used for sealing the bottom end of the first cylinder, the second disc partition plate 18 is used for sealing the top end of the second cylinder, the air suction notch 13 is a first air suction notch formed in the first disc partition plate 17 and a second air suction notch formed in the second disc partition plate 18, and the air suction piece is a partition plate 6 which is arranged between the first cylinder and the second cylinder and sleeves the first disc partition plate 17 and the second disc partition plate 18 into the cavity 8. As shown in fig. 18-20.
Further, in order to avoid the intake contention phenomenon of the two cylinders, the first intake gap and the second intake gap are circumferentially offset from each other, and preferably, the angle between the two intake gaps is 90 °, as shown in fig. 19, and the gap between the first disk partition 17 and the second disk partition 18 forms an airflow passage, and the arrows in fig. 18 represent the airflow direction. It can be understood that, because the bottom end of the first cylinder is matched with the first disk partition 17, the exhaust port of the first cylinder is arranged on the upper flange, and the top end of the second cylinder is matched with the second disk partition 18, the exhaust port of the second cylinder is arranged on the lower flange, and the partition 6 also has the function of an air suction piece.
The working process of the compressor in the embodiment is as follows: refrigerant gas enters an airflow channel formed by the disc partition plate 9 and the cavity of the partition plate 6 through the suction port of the partition plate 6, and the refrigerant gas entering the airflow channel enters working cavities of the first cylinder and the second cylinder through the first suction notch and the second suction notch respectively to be compressed.
Third embodiment
Referring to fig. 21, in the rotary compressor disclosed in the present embodiment, the multi-sliding-vane cylinder and the other single-sliding-vane cylinder in embodiment 1 are included, and the two cylinders form multi-stage compression, and it is easily understood by those skilled in the art that any one of the multi-sliding-vane cylinder and the single-sliding-vane cylinder may be used as a low-pressure stage cylinder, for example, when the exhaust port of the multi-sliding-vane cylinder is communicated with the suction port of the single-sliding-vane cylinder, the multi-sliding-vane cylinder corresponds to a low-pressure stage cylinder, and refrigerant gas compressed in the multi-sliding-vane cylinder is sucked into the single-sliding-vane cylinder for further compression, so the single-sliding-vane cylinder corresponds to a high-pressure stage cylinder; of course, if the air suction port of the multi-sliding-vane cylinder is communicated with the air exhaust port of the single-sliding-vane cylinder, the multi-sliding-vane cylinder becomes a high-pressure cylinder, and the single-sliding-vane cylinder becomes a low-pressure cylinder.
Since the multi-stage compressor is a known technology of those skilled in the art, in this embodiment, at least one stage of the multi-stage compressor is mainly replaced by a multi-sliding-vane cylinder, and therefore, how to connect the cylinders is not described herein again.
Fourth embodiment
Referring to fig. 22, in the multi-sliding-vane cylinder of the present embodiment, three sliding vanes are disposed uniformly in the cylinder body, so that the compressor has less vibration and operates more stably.
It should be noted that the present invention has been described separately for the above embodiments, and the above embodiments can be freely combined and overlapped without contradiction, and the compressor in the present invention is not limited to the vertical compressor, and is also applicable to the horizontal compressor.
Besides, the embodiment of the invention also discloses a refrigeration system, which comprises a compressor, a condenser 22, a throttling device 23 and an evaporator 24, wherein the compressor in the refrigeration system is the rotary compressor disclosed in any one of the embodiments.
The temperature adjusting device disclosed in the embodiment of the invention comprises an air conditioner and a refrigerator, and the refrigerating system in the temperature adjusting device is the refrigerating system disclosed in the embodiment.
It should be noted that the refrigeration system in the embodiment of the present invention is a general term, and heating can be achieved even when a four-way valve is added to the refrigeration system, and therefore, the refrigeration system also includes a system that can heat after the four-way valve is added.
The rotary compressor, the refrigerating system and the temperature adjusting device of the present invention are described in detail above. The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the method and its core concepts. It should be noted that, for those skilled in the art, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.

Claims (6)

1. A rotary compressor comprising two multiple-sliding-vane cylinders, characterized in that said multiple-sliding-vane cylinders comprise:
a cylinder body (5);
a plurality of sliding vanes (11) arranged in the cylinder body (5);
the sliding vane type compressor comprises a crankshaft (1) and a rotor (3) which is arranged on the crankshaft (1) and matched with the sliding vane (11);
the disc partition plate (9) is fixedly connected to the crankshaft (1), and the disc partition plate (9) is used for sealing the bottom end or the top end of the cylinder body (5);
the air suction gap (13) is formed in the outer circle of the disc partition plate (9), and when the volume of a working cavity in the cylinder body (5) is increased, the air suction gap (13) is communicated with the working cavity; when the volume of the working chamber is reduced, the disc partition plate (9) closes the working chamber;
the multiple-sliding-vane cylinder further comprises:
the air suction piece is provided with an air suction port (12), a cavity (8) is arranged inside the air suction piece, and the inner wall of the cavity is matched with the outer circle of the disc partition plate (9) to form an air suction cavity communicated with the air suction port (12);
the two multi-sliding-vane cylinders are respectively a first cylinder and a second cylinder which are arranged along the axial direction of the compressor, the disc clapboard (9) is a first disc clapboard (17) and a second disc clapboard (18) which are arranged at intervals, wherein the first disc partition plate (17) is used for closing the bottom end of the first cylinder, the second disc partition plate (18) is used for closing the top end of the second cylinder, the air suction gap (13) is a first air suction gap arranged on the first disc clapboard (17), and a second air suction gap arranged on the second disc clapboard (18), the air suction piece is arranged between the first air cylinder and the second air cylinder, and the first disc partition plate (17) and the second disc partition plate (18) are sleeved into the partition plate (6) in the cavity, and the first air suction gap and the second air suction gap are staggered.
2. The rotary compressor of claim 1, wherein an angle between the first suction notch and the second suction notch is 90 °.
3. A rotary compressor according to any one of claims 1-2, characterized in that two said sliding vanes (11) are provided in any one of said cylinders.
4. A refrigeration system comprising a compressor, a condenser, a throttling device and an evaporator, characterized in that the compressor is a rotary compressor according to any one of claims 1-3.
5. Tempering device provided with a refrigeration system, characterized in that the refrigeration system is a refrigeration system according to claim 4.
6. Tempering device according to claim 5, characterized in that the tempering device is an air conditioner or a refrigerator.
CN201710008622.2A 2017-01-05 2017-01-05 Rotary compressor, refrigerating system and temperature adjusting equipment Active CN106837790B (en)

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