EP4174318A1 - Rotary compressor and refrigeration cycle device - Google Patents
Rotary compressor and refrigeration cycle device Download PDFInfo
- Publication number
- EP4174318A1 EP4174318A1 EP21834557.7A EP21834557A EP4174318A1 EP 4174318 A1 EP4174318 A1 EP 4174318A1 EP 21834557 A EP21834557 A EP 21834557A EP 4174318 A1 EP4174318 A1 EP 4174318A1
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- EP
- European Patent Office
- Prior art keywords
- intake
- piston
- cylinder
- rotary compressor
- vane
- 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.)
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 15
- 230000006835 compression Effects 0.000 claims abstract description 52
- 238000007906 compression Methods 0.000 claims abstract description 52
- 238000005192 partition Methods 0.000 claims abstract description 20
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 16
- 239000012530 fluid Substances 0.000 claims description 11
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 8
- 239000001569 carbon dioxide Substances 0.000 claims description 8
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 5
- 239000007789 gas Substances 0.000 description 30
- 239000003507 refrigerant Substances 0.000 description 13
- 238000004891 communication Methods 0.000 description 9
- 238000000034 method Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 238000005096 rolling process Methods 0.000 description 6
- 239000007788 liquid Substances 0.000 description 4
- 230000009191 jumping Effects 0.000 description 3
- 239000003990 capacitor Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000008014 freezing Effects 0.000 description 2
- 238000007710 freezing Methods 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 239000000470 constituent Substances 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000001151 other effect Effects 0.000 description 1
- 230000008447 perception Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
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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
- 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
- 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
- F04C2240/80—Other components
- F04C2240/806—Pipes for fluids; Fittings therefor
Definitions
- Patent document 1 discloses a rotary compressor which reliably prevents a vane from jumping.
- This rotary compressor includes a cylinder whose both end openings are closed, a piston which rotates in the cylinder, a vane which forms a compression space together with the piston and the cylinder and which partitions the space into a high pressure side and a low pressure side, and connecting means for swingably connecting the piston and the vane to each other.
- the rotary compressor 200 includes a drive shaft 201, the upper piston 2021, the lower piston 2022, the upper cylinder 2031, the lower cylinder 2032, an upper bearing 204, a lower bearing 205, upper and lower vanes, the upper intake hole 2071a, the lower intake hole 2072a and a partition plate 221.
- Upper and lower compression elements are configured in the axial direction.
- the partition plate 221 is provided between the upper and lower compression elements.
- An upper bearing 204 and the lower bearing 205 support the drive shaft 201.
- the upper intake hole 2071a is provided in the upper bearing 204
- the lower intake hole 2072a is provided in the lower bearing 205.
- a rotary compressor 300 of the third embodiment is different from the rotary compressor 200 of the second embodiment at least in that a partition plate 321 is provided with an intake hole 307a instead of an upper bearing 304 and a lower bearing 305.
- the rotary compressor 100 of one cylinder and the rotary compressors 200 and 300 of two cylinders are described as one examples of the rotary compressor. It is only necessary that the rotary compressor compresses gas. Therefore, the rotary compressor is not limited to the rotary compressor 100 of one cylinder or the rotary compressors 200 and 300 of two cylinders. However, if the rotary compressor 100 of one cylinder or the rotary compressors 200 and 300 of two cylinders are used, there are merits that balance between costs, efficiency and reliability is kept and volume production can be made. As the rotary compressor, a two-stage compressor may be used.
- one cylinder may include a plurality of vanes and compression chambers. If this is used, torque variation can be reduced by carrying out the compression action which is substantially the same as that of the two-cylinder type in the configuration of the rotary compressor 100 of the one cylinder, and a pressure difference can be reduced if the two-stage compression configuration is employed. Therefore it is possible to realize a rotary compressor capable of carrying out low vibration and high pressure ratio operation with the small number of parts.
- vane 106 having the engaging portion 106a which is swingably fitted into and connected to the engaging groove 102a formed in the piston 102 was described as one example of the vane.
- the vane partitions the intake chamber and the compression chamber from each other, the vane is always operated integrally with the piston, and a spring is unnecessary on the back surface of the vane. Therefore, the vane is not limited to the vane 106 including the engaging portion 106a which is swingably fitted into and connected to the engaging groove 102a formed in the piston 102.
Abstract
Description
- The present disclosure relates to a rotary compressor and a refrigeration cycle device using the rotary compressor of an air conditioner, a freezing machine, a blower, a hot water supply system and the like.
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Patent document 1 discloses a rotary compressor which reliably prevents a vane from jumping. This rotary compressor includes a cylinder whose both end openings are closed, a piston which rotates in the cylinder, a vane which forms a compression space together with the piston and the cylinder and which partitions the space into a high pressure side and a low pressure side, and connecting means for swingably connecting the piston and the vane to each other. - [Patent Document 1]
Japanese Patent Application Laid-open No.2000-120572 - The present disclosure provides a rotary compressor and a refrigeration cycle device in which a height of a cylinder is lowered to reduce leakage loss and a cross-sectional area of an intake passage is secured to suppress increase in pressure loss.
- Each of a rotary compressor and a refrigeration cycle device of the present disclosure includes: a drive shaft including an eccentric shaft; a piston fitted into the eccentric shaft; a cylinder accommodating the piston which eccentrically rotates; an upper end plate and a lower end plate which close upper and lower opening surfaces of the cylinder; a vane which partitions a space formed by the cylinder, the piston and the upper and lower end plates into an intake chamber and a compression chamber, and which is integrally operated with the piston; and an intake hole which is provided at least in one of the upper and lower end plates, and to which an intake pipe is connected, and intake gas being introduced from outside of the compressor into the intake chamber through the intake pipe.
- According to the rotary compressor and the refrigeration cycle device of the disclosure, a height of the cylinder can be lowered by increasing an inner diameter of the cylinder. Therefore, a cross-sectional area of a leakage gap between an inner periphery of the cylinder and an outer periphery of the piston is reduced to reduce leakage loss, and efficiency of the compressor can be enhanced. Further, since the intake passage is provided in any one of the upper and lower end plates, it is possible to secure an area of the intake passage, and to suppress the increase in pressure loss.
-
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Fig. 1 is a vertical sectional view of a rotary compressor in a first embodiment of the present invention; -
Fig. 2 is a lateral sectional view of a compression mechanism in the first embodiment of the invention; -
Fig. 3 is an explanatory diagram of compressing action of the compression mechanism in the first embodiment of the invention; -
Fig. 4 is a vertical sectional view of a rotary compressor in a second embodiment of the invention; and -
Fig. 5 is a vertical sectional view of a rotary compressor in a third embodiment of the invention. - When the present inventors achieved the present disclosure, a back surface of a vane of a rotary compressor was provided with a spring, the vane was pressed against a piston by a spring force and a pressure difference, and a compression chamber was formed by pressing action of the vane to carry out the compression. However, according to the conventional rolling type rotary compressor, the vane jumps by shortage of a pressing force under a load condition such as low compression ratio. Therefore, the rolling piston type has a problem that noise is deteriorated by collision between the vane and the piston, and performance is deteriorated by leakage from a gap between the vane and the piston.
- Hence, there is conventionally proposed a technique in which a piston and a vane are swingably connected to each other and they are integrally operated to carry out the compression to prevent the vane from jumping. According to this, there are effects that it is possible not only to solve the above-described problem, but also eliminate the spring because it is unnecessary to press the vane by the spring, and reduce the number of parts and the number of assembling steps, and material costs are directly suppressed.
- Further, according to a rotary compressor in which the piston and the vane integrally operate to carry out the compression, since a space for accommodating a spring is unnecessary, the vane can be placed on a more outer side as compared with the above-described rolling piston type rotary compressor. Hence, according to the rotary compressor, an inner diameter of the cylinder can be set larger and a height of the cylinder can be set lower. According to this, a cross-sectional area of a leakage gap of a seal portion between an outer periphery of the piston and an inner periphery of the cylinder can be made small, and leakage loss can be reduced.
- However, if the height of the cylinder is set low, a diameter of the intake passage which is provided on the side of the outer periphery of the cylinder, and through which intake gas is introduced from outside of the compressor becomes small, and a sufficient cross-sectional area of the intake passage cannot be secured. Therefore, there are problems that pressure loss is increased in the intake procedure and efficiency of the compressor is deteriorated.
- The present inventors found such a problem, and configured a subject matter of the present disclosure to solve the problem.
- Hence, the disclosure provides a rotary compressor in which a height of the cylinder is lowered, leakage loss is reduced, a cross-sectional area of the intake passage is secured, and increase in pressure loss is suppressed.
- Embodiments will be described below with reference to the drawings. However, description which is detail more than necessary will be omitted in some cases. For example, detailed description of already well known matters, or redundant description of substantially the same configuration will be omitted in some cases. This is for preventing the following description from becoming redundant more than necessary, and for making it easy for a person skilled in the art to understand the present disclosure.
- The accompanying drawing and the following description are provided so that a person skilled in the art can sufficiently understand the present disclosure, and it is not intended that they limit the subject matter described in claims.
- A first embodiment will be described below using
Figs. 1 to 3 . - In
Figs. 1 and2 , arotary compressor 100 includes adrive shaft 101, apiston 102, acylinder 103, an upper end plate (upper bearing, hereinafter) 104 having a function as an upper bearing, a lower end plate (lower bearing, hereinafter) 105 having a function as a lower bearing, avane 106 and anintake hole 107a. - An entire interior of a hermetic container 108 is discharge pressure atmosphere which is in communication with a
discharge pipe 109. Anelectric motor 110 is accommodated in a central portion of the hermetic container 108, and acompression mechanism 111 is accommodated in a lower portion of the hermetic container 108. Thecompression mechanism 111 is driven by thedrive shaft 101 which is fixed to a rotor 110a of theelectric motor 110. - In the
compression mechanism 111, thecylinder 103, thepiston 102 and thevane 106 are sandwiched between theupper bearing 104 and thelower bearing 105, a space formed between thecylinder 103 and thepiston 102 is partitioned by thevane 106, thereby forming anintake chamber 112 and acompression chamber 113, and compressing action is carried out. - An eccentric shaft 101a which is integrally formed with the
drive shaft 101 is accommodated in thecylinder 103, and thepiston 102 is rotatably attached to the eccentric shaft 101a. An engaging groove 102a is formed in an outer periphery of thepiston 102. An engaging portion 106a is formed on a tip end of thevane 106, and thevane 106 is swingably connected to thepiston 102. There is not a spring which is provided on a back surface of thevane 106 of a conventional rolling piston type compressor. - The
upper bearing 104 is provided with anintake passage 107 which is composed of aradial intake hole 107a and an axial vertical hole 107b. Theintake passage 107 is in communication with theintake chamber 112. Anintake liner 114 is press-fitted into theintake hole 107a. Theintake liner 114 separates high temperature and high pressure discharge gas in the hermetic container 108 and low temperature and low pressure intake gas in theintake hole 107a. - An
accumulator 115 for preventing liquid of the compressor from being compressed is inserted into theintake liner 114. Theaccumulator 115 is connected together with an intakeouter pipe 116 with wax or welding. The intakeouter pipe 116 is fixed to the hermetic container 108. Working fluid is sucked into therotary compressor 100. Theaccumulator 115 separates the working fluid into gas and liquid. - That is, the first embodiment is configured such that intake gas from outside of the
compressor 100 is introduced into theintake chamber 112 through an intake pipe which is composed of theintake liner 114 and the intakeouter pipe 116. Theaccumulator 115 is inserted into theintake liner 114. The intake pipe may be composed of only theaccumulator 115 and the intakeouter pipe 116, and theaccumulator 115 may be connected directly to theintake hole 107a. - The
rotary compressor 100 of the first embodiment uses carbon dioxide as the working fluid. - Action of the
rotary compressor 100 configured as described above will be described below based onFigs. 1 and3 . -
Fig. 3 is a diagram for explaining volume variations of theintake chamber 112 and thecompression chamber 113 whenever the crank angle is changed by 90°, and the volume is changed in directions of open arrows. Theintake passage 107 of theupper bearing 104 which is not illustrated inFig. 3 is located on the left side of thevane 106, and theintake passage 107 is in communication with theintake chamber 112. - If the
electric motor 110 is biased and thedrive shaft 101 rotates, the eccentric shaft 101a eccentrically rotates in thecylinder 103, and theconnected piston 102 and thevane 106 integrally operate. According to this, suction action and compression action of the working fluid are repeated. - Low temperature and low pressure gas is sucked into the
intake chamber 112 through theaccumulator 115, theintake liner 114 and theintake passage 107. The low temperature and low pressure intake gas is compressed by thecompression mechanism 111. The compressed high temperature and high pressure gas passes through a discharge hole (not shown) which is provided in theupper bearing 104 and which is in communication with thecompression chamber 113, and the gas is discharged into a muffler chamber 117 (seeFig. 1 ) through a check valve. Thereafter, the discharge gas passes through each gap of a small hole provided in a muffler 118, an electric motor lower space 119 located between thecompression mechanism 111 and theelectric motor 110, and theelectric motor 110. Then, the discharge gas is guided into an electric motorupper space 120, and discharged from therotary compressor 100 through thedischarge pipe 109. - Oil is stored in a lower portion of the hermetic container 108, and the
compression mechanism 111 is normally immersed in oil. An oil passage (not shown) is provided in thedrive shaft 101 in its axial direction. Oil pumped up from a lower end of the oil passage passes through a refueling hole (not shown) provided in the eccentric shaft 101a, lubricates a sliding portion of the eccentric shaft 101a, and reaches an inner periphery of thepiston 102. Then, one portion of the oil lubricates journal bearing sliding portions of theupper bearing 104 and thelower bearing 105, and is discharged to outside of thecompression mechanism 111. The other portion of the oil lubricates upper and lower end surfaces of thepiston 102 and sliding portions of theupper bearing 104 and thelower bearing 105, and is supplied to theintake chamber 112 and thecompression chamber 113. - Oil supplied from a back surface of the
vane 106 lubricates a sliding portion of thevane 106 and thereafter, the oil is supplied to theintake chamber 112 and thecompression chamber 113. The oil in theintake chamber 112 and thecompression chamber 113 is discharged out from a discharge hole 121 together with gas and then, the oil moves into a current of the gas and reaches thedischarge pipe 109. In the meantime, most of oil is separated from discharge gas and liquidized, and returns to a lower portion of the hermetic container 108 by gravity. - As described above, in the embodiment, the
rotary compressor 100 includes thedrive shaft 101, thepiston 102, thecylinder 103, theupper bearing 104, thelower bearing 105, thevane 106 and theintake hole 107a. Thedrive shaft 101 includes the eccentric shaft 101a. Thepiston 102 is fitted into the eccentric shaft 101a. Thepiston 102 which eccentrically rotates is accommodated in thecylinder 103. Theupper bearing 104 and thelower bearing 105 close upper and lower opening surfaces of thecylinder 103. A space is formed by thecylinder 103, thepiston 102, theupper bearing 104 and thelower bearing 105. Thevane 106 partitions this space into theintake chamber 112 and thecompression chamber 113, and thevane 106 integrally operates with thepiston 102. Theintake hole 107a is not provided in thecylinder 103 but is provided in theupper bearing 104, and theintake liner 114 and theaccumulator 115 are connected to theintake hole 107a. Theintake liner 114 and theaccumulator 115 introduce intake gas from therotary compressor 100 into theintake chamber 112. - According to this, in the case of the conventional rolling piston type compressor, a spring is required on the back surface of the
vane 106, but in the case of therotary compressor 100, a spring is not required. Correspondingly, the inner diameter D of thecylinder 103 can be made large, and the height H thereof can be lowered. Hence, a cross-sectional area of the leakage gap of a contact point seal portion between the outer periphery of thepiston 102 and the inner periphery of thecylinder 103 is reduced, and leakage loss from thecompression chamber 113 into theintake chamber 112 can be reduced. Simultaneously, theintake hole 107a has a sufficiently large diameter, and the cross-sectional area of theintake passage 107 can be secured. Therefore, when theintake hole 107a having a small diameter is provided in thecylinder 103 having low height H, pressure loss is generated in theintake passage 107, but the pressure loss is not increased, and efficiency of the compressor can be enhanced. - The
rotary compressor 100 of the embodiment uses carbon dioxide as the working fluid. - According to this carbon dioxide refrigerant, a pressure difference between the
intake chamber 112 and thecompression chamber 113 is larger than that of other refrigerant such as HFC-based refrigerant, HC-based refrigerant and HFO-based refrigerant. Hence, influence in which leakage loss at the seal portion between thepiston 102 and thecylinder 103 exerts on compressor efficiency is large. However, according to the configuration of the present disclosure, since the height H of thecylinder 103 can be set extremely low, the area of the seal portion between thepiston 102 and thecylinder 103 can be reduced. Therefore, it is possible to more effectively reduce the leakage loss and to enhance the compressor efficiency. - According to the
rotary compressor 100 of the embodiment, a ratio D/H of the inner diameter D and the height H of thecylinder 103 is in a range of 2 to 13. - According to this, it is possible to avoid a case in which the above-described effect is lowered because D/H is too small, and a case in which the surface areas of the
intake chamber 112 and thecompression chamber 113 are increased because D/H is too large and the heat receiving loss is increased. Hence, it is possible to enhance the compressor efficiency at a maximum. - It is more preferable that the D/H is in a range of 2 to 8.
- According to this, it is possible to avoid a case in which a distance between an axis of the
drive shaft 101 and an axis of the eccentric shaft 101a, i.e., an eccentric amount becomes extremely large and insertion performance of thepiston 102 is deteriorated. Hence, it is possible to realize theefficient rotary compressor 100 which can easily be assembled. - According to the
rotary compressor 100 of the embodiment, the engaging groove 102a is formed in thepiston 102 and the engaging portion 106a is provided on a tip end of thevane 106. The engaging portion 106a is swingably connected by fitting the engaging portion 106a into the engaging groove 102a of thepiston 102. - According to this, it is unnecessary to largely change a design of the
piston 102, and the number of parts is not increased. Therefore, increase of costs can be suppressed to the minimum. - The
rotary compressor 100 of the embodiment is used in a refrigeration cycle device. Since thepiston 102 and thevane 106 are connected to each other using the above-described configuration, jumping of the vane which is the problem in the conventional rolling piton type is not generated, and it is possible to reduce noise and enhance efficiency. Hence, the rotary compressor and the refrigeration cycle device can be operated under an operation condition such as low pressure compression ratio. Since the operation range of therotary compressor 100 is widened, a freedom degree of the operation of the refrigeration cycle device is enhanced, and system efficiency can be enhanced. - The
rotary compressor 100 of the embodiment is used in a heat pump hot water supply system. - Temperature of discharge gas of the heat pump hot water supply system is higher than that of other refrigeration cycle device. Hence, temperature of the
lower bearing 105 which is exposed to high temperature discharge gas becomes high, thelower bearing 105 receives heat of low temperature intake gas which passes through theintake passage 107, and volume efficiency is deteriorated. However, in the rotary compressor of the disclosure, since the inner diameter D of thecylinder 103 is large, i.e., since a distance between an inner wall of the hermetic container 108 and an inner wall of thecylinder 103 is short, a length of theintake passage 107 is also short. Hence, heat of intake gas is less prone to be received, and volume efficiency can more effectively be enhanced. - A second embodiment will be described below using
Fig. 4 . - In a
rotary compressor 200 of the second embodiment, two cylinders, i.e., an upper cylinder 2031 and alower cylinder 2032 are constituted, and apartition plate 221 is provided between the upper cylinder 2031 and thelower cylinder 2032. This point is different from therotary compressor 100 composed of the onecylinder 103 in the first embodiment. - The upper cylinder 2031, an
upper piston 2021 and an upper vale (not shown) are sandwiched between anupper bearing 204 and apartition plate 221, thelower cylinder 2032, alower piston 2022 and a lower vane (not shown) are sandwiched between thepartition plate 221 and alower bearing 205, and a space formed between the upper andlower cylinders 2031, 2032 and the upper andlower pistons - The
upper bearing 204 is provided with anupper intake passage 2071. Theupper intake passage 2071 is composed of a radial upper intake hole 2071a and an axial and an axial upper vertical hole 2071b, and theupper intake passage 2071 is in communication with the upper intake chamber 2121. Thelower bearing 205 is provided with thelower intake passage 2072. Thelower intake passage 2072 is composed of a radial lower intake hole 2072a and an axial lower vertical hole 2072b, and thelower intake passage 2072 is in communication with the lower intake chamber 2122. - A trapping volume of the
rotary compressor 200 is the same as that of therotary compressor 100 of the first embodiment, but since the twocylinders 2031 and 2032 share the volume, height Hu and Hl of thecylinders 2031 and 2032 are lower than the height H of thecylinder 103 of therotary compressor 100 of the first embodiment. - Action of the
rotary compressor 200 configured as described above will be described below. - Intake gas which is separated into gas and liquid by an
accumulator 215 branches into two pipes, and is sucked from the upper andlower intake passages - Compressing actions of the completion elements of the
rotary compressor 200 are the same as those of therotary compressor 100 of the first embodiment. However, upper lower compression chambers 2131 and 2132 carry out completion in opposite phase. - Lower discharge gas compressed by the
lower cylinder 2032 flows into amuffler chamber 217 through a communication passage (not shown), and joins up with upper discharge gas which is compressed by the upper cylinder 2031. Flow of the discharge gas thereafter is the same as that of therotary compressor 100 of the first embodiment. - As described above, in this embodiment, the
rotary compressor 200 includes adrive shaft 201, theupper piston 2021, thelower piston 2022, the upper cylinder 2031, thelower cylinder 2032, anupper bearing 204, alower bearing 205, upper and lower vanes, the upper intake hole 2071a, the lower intake hole 2072a and apartition plate 221. Upper and lower compression elements are configured in the axial direction. Thepartition plate 221 is provided between the upper and lower compression elements. Anupper bearing 204 and thelower bearing 205 support thedrive shaft 201. The upper intake hole 2071a is provided in theupper bearing 204, and the lower intake hole 2072a is provided in thelower bearing 205. - According to this, by carrying out compression by the upper and
lower pistons rotary compressor 100 of the first embodiment, and reduce vibration. Inner diameters D of the upper cylinder 2031 and the lower cylinder 203 are increased and heights Hu and Hl are reduced. Therefore, cross-sectional areas of leakage gases between outer peripheries of thepistons cylinders 2031 and 2032 and contact point seal portion are further reduced, and leakage loss from the compression chambers 2131 and 2132 into the intake chambers 2121 and 2122 can be reduced. In addition, theupper bearing 204 and thelower bearing 205 are provided with the upper intake hole 2071a and the lower intake hole 2072a. According to this, diameters of the intake holes 2071a and 2072a can sufficiently be increased, and cross-sectional areas of theintake passages cylinders 2031 and 2032 having low heights Hu and Hl are provided with the intake holes 2071a and 2072a having small diameters, pressure loss is generated in theintake passages - A third embodiment will be described below using
Fig. 5 . - A
rotary compressor 300 of the third embodiment is different from therotary compressor 200 of the second embodiment at least in that a partition plate 321 is provided with an intake hole 307a instead of anupper bearing 304 and alower bearing 305. - The partition plate 321 is provided with an
intake passage 307. Theintake passage 307 is composed of a radial intake hole 307a, an upper vertical hole 307b which is in communication with an upper intake chamber 3121, and a lower vertical hole 307c which is in communication with a lower intake chamber 3122 (not numbered). - Action of the
rotary compressor 300 configured as described above will be described below. - Intake gas which is separated into gas and liquid in an
accumulator 315 is distributed into upper and lower portions in theintake passage 307, and is sucked into upper and lower intake chambers 3121 and 3122. - Gas sucked into the upper and lower intake chambers 3121 and 3122 is compressed in the same manner as that of the second embodiment.
- As described above, in the embodiment, the
rotary compressor 300 includes adrive shaft 301, anupper piston 3021, alower piston 3022, anupper cylinder 3031, a lower cylinder 3032, anupper bearing 304, alower bearing 305, upper and lower vanes, the intake hole 307a and the partition plate 321. Upper and lower compression elements are configured in the axial direction. The partition plates 321 is provided between the upper and lower compression elements. Theupper bearing 304 and thelower bearing 305 support thedrive shaft 301. The partition plate 321 is provided with the intake hole 307a. - According to this, the
accumulator 115 of therotary compressor 100 in which onecylinder 103 of the first embodiment is configured can be used as it is. Hence, as compared with therotary compressor 200 of the second embodiment, the number of parts and the number of assembling steps can be reduced, and it is possible to realize theinexpensive accumulator 315 and theinexpensive rotary compressor 300. Other effects are the same as those of the second embodiment. - As described above, the first to third embodiments are described as examples of techniques disclosed in the present application. However, the technique in this disclosure is not limited to this, and the technique can be applied to changed, replaced, added and omitted embodiments also. Further, constituent elements described in the above first to third embodiments can be combined as new embodiments.
- Other embodiments will be described below.
- In the first to third embodiments, the
rotary compressor 100 of one cylinder and therotary compressors rotary compressor 100 of one cylinder or therotary compressors rotary compressor 100 of one cylinder or therotary compressors rotary compressor 100 of the one cylinder, and a pressure difference can be reduced if the two-stage compression configuration is employed. Therefore it is possible to realize a rotary compressor capable of carrying out low vibration and high pressure ratio operation with the small number of parts. - In the first embodiment,
vane 106 having the engaging portion 106a which is swingably fitted into and connected to the engaging groove 102a formed in thepiston 102 was described as one example of the vane. The vane partitions the intake chamber and the compression chamber from each other, the vane is always operated integrally with the piston, and a spring is unnecessary on the back surface of the vane. Therefore, the vane is not limited to thevane 106 including the engaging portion 106a which is swingably fitted into and connected to the engaging groove 102a formed in thepiston 102. However, if this is used, it is unnecessary to largely change the design of thepiston 102 as described above, and the number of parts is not increased and therefore, increase of costs can be suppressed to the minimum. As the vane, if a swing type vane which is completely integrally formed with the piston and in which the piston is swingably operated through a swinging bush provided in the cylinder is used, there is no contact point between the vane and the piston. Hence, leakage loss and sliding loss are eliminated completely in a very small gap, and efficiency of therotary compressor 100 can be enhanced. - Further, in the first embodiment, carbon dioxide is described as one example of working fluid. Any working fluid may be used only if compressible fluid. Therefore, the working fluid is not limited to carbon dioxide. However, if carbon dioxide is used, a pressure difference between the
intake chamber 112 and thecompression chamber 113 is large as compared with other refrigerant such as HFC-based refrigerant, HC-based refrigerant and HFO-based refrigerant as described above, and influence in which leakage loss exerts on the efficiency of the compressor at the seal portion between thepiston 102 and thecylinder 103 is large. However, if the height H of thecylinder 103 is set extremely low using the configuration of this disclosure, leakage loss can more effectively be reduced. Further, if mixture refrigerant of other HFO-based refrigerant and carbon dioxide is used to the HFC-based refrigerant and HC-based refrigerant as working fluid, it is possible to suppress temperature glide between an inlet and an outlet of a capacitor of the refrigeration cycle. Hence, it is possible to suppress the deterioration of heat exchanging efficiency of the capacitor. - The above-described embodiments are for exemplifying the techniques of the disclosure and therefore, the embodiments can variously be changed, replaced, added and omitted within patent claims and equable scope.
- The present disclosure can be applied to a rotary compressor and a refrigeration cycle device in which leakage loss and pressure loss are generated. More specifically, the present disclosure can be applied to an air conditioner, a freezing machine, a blower, a hot water supply system and the like.
-
- 100
- rotary compressor
- 101, 201, 301
- drive shaft
- 101a
- eccentric shaft
- 102
- piston
- 102a
- engaging groove
- 103
- cylinder
- 104, 204, 304
- upper bearing (upper end plate)
- 105, 205, 305
- lower bearing (lower end plate)
- 106
- vane
- 106a
- engaging portion
- 107
- intake passage
- 107a
- intake hole
- 107b
- vertical hole
- 108
- hermetic container
- 109
- discharge pipe
- 110
- electric motor
- 110a
- rotor
- 110b
- stator
- 111
- compression mechanism
- 112
- intake chamber
- 113
- compression chamber
- 114
- intake liner (intake pipe)
- 115
- accumulator (intake pipe)
- 116
- intake outer pipe (intake pipe)
- 117
- muffler chamber
- 118
- muffler
- 119
- electric motor lower space
- 120
- electric motor upper space
- 200
- rotary compressor
- 2021
- upper piston
- 2022
- lower piston
- 2031
- upper cylinder
- 2032
- lower cylinder
- 2071
- upper intake passage
- 2071a
- upper intake hole
- 2071b
- upper vertical hole
- 2072
- lower intake passage
- 2072a
- lower intake hole
- 2072b
- lower vertical hole
- 2121
- upper intake chamber
- 2122
- lower intake chamber
- 2131
- upper compression chamber
- 2132
- lower compression chamber
- 215
- accumulator
- 217
- muffler chamber
- 221
- partition plate
- 300
- rotary compressor
- 3021
- upper piston
- 3022
- lower piston
- 3031
- upper cylinder
- 3032
- lower cylinder
- 307
- intake passage
- 307a
- intake hole
- 307b
- upper vertical hole
- 307c
- lower vertical hole
- 3121
- upper intake chamber
- 3122
- lower intake chamber
- 315
- accumulator
- 321
- partition plate
Claims (7)
- A rotary compressor comprising:a drive shaft including an eccentric shaft;a piston fitted into the eccentric shaft;a cylinder accommodating the piston which eccentrically rotates;an upper end plate and a lower end plate which close upper and lower opening surfaces of the cylinder;a vane which partitions a space formed by the cylinder, the piston and the upper and lower end plates into an intake chamber and a compression chamber, and which is integrally operated with the piston; andan intake hole which is provided at least in one of the upper and lower end plates, and to which an intake pipe is connected, and intake gas being introduced from outside of the compressor into the intake chamber through the intake pipe.
- The rotary compressor according to claim 1, further comprising:a plurality of compression elements in an axial direction of the rotary compressor, the compression elements being composed of the cylinder, the piston and the vane; anda partition plate located between the plurality of compression elements; whereinupper and lower bearings which support the drive shaft at upper and lower locations, and the partition plate are configured as the upper and lower end plates.
- The rotary compressor according to claim 1 or 2, wherein
carbon dioxide is used as working fluid. - The rotary compressor according to any one of claims 1 to 3, wherein a ratio D/H of an inner diameter D and a height H of the cylinder is in a range of 2 to 13.
- The rotary compressor according to any one of claims 1 to 4, further comprising:an engaging groove formed in the piston; andan engaging portion provided on a tip end of the vane and swingably fitted into and connected to the engaging groove.
- A refrigeration cycle device comprising the rotary compressor according to any one of claims 1 to 5.
- The refrigeration cycle device according to claim 6, wherein the refrigeration cycle device is a heat pump hot water supply system.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2020111037 | 2020-06-29 | ||
PCT/JP2021/001772 WO2022004028A1 (en) | 2020-06-29 | 2021-01-20 | Rotary compressor and refrigeration cycle device |
Publications (2)
Publication Number | Publication Date |
---|---|
EP4174318A1 true EP4174318A1 (en) | 2023-05-03 |
EP4174318A4 EP4174318A4 (en) | 2023-12-13 |
Family
ID=79315186
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP21834557.7A Pending EP4174318A4 (en) | 2020-06-29 | 2021-01-20 | Rotary compressor and refrigeration cycle device |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP4174318A4 (en) |
JP (1) | JPWO2022004028A1 (en) |
CN (1) | CN115190944A (en) |
WO (1) | WO2022004028A1 (en) |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0381592A (en) * | 1989-08-24 | 1991-04-05 | Mitsubishi Electric Corp | Two-cylinder rotary compressor |
JPH09250477A (en) * | 1996-03-18 | 1997-09-22 | Toshiba Corp | Rotary compressor |
JP2000120572A (en) | 1998-10-12 | 2000-04-25 | Sanyo Electric Co Ltd | Rotary compressor |
JP4289975B2 (en) * | 2003-11-05 | 2009-07-01 | 三洋電機株式会社 | Multi-stage rotary compressor |
KR101442550B1 (en) * | 2008-08-06 | 2014-09-22 | 엘지전자 주식회사 | Rotary compressor |
JP2010255624A (en) * | 2009-03-31 | 2010-11-11 | Panasonic Corp | Rotary compressor |
-
2021
- 2021-01-20 EP EP21834557.7A patent/EP4174318A4/en active Pending
- 2021-01-20 WO PCT/JP2021/001772 patent/WO2022004028A1/en unknown
- 2021-01-20 JP JP2022533665A patent/JPWO2022004028A1/ja active Pending
- 2021-01-20 CN CN202180017156.9A patent/CN115190944A/en active Pending
Also Published As
Publication number | Publication date |
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EP4174318A4 (en) | 2023-12-13 |
JPWO2022004028A1 (en) | 2022-01-06 |
CN115190944A (en) | 2022-10-14 |
WO2022004028A1 (en) | 2022-01-06 |
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