CN107110160A - Multi-cylinder hermetic type compressor - Google Patents
Multi-cylinder hermetic type compressor Download PDFInfo
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- CN107110160A CN107110160A CN201580061211.9A CN201580061211A CN107110160A CN 107110160 A CN107110160 A CN 107110160A CN 201580061211 A CN201580061211 A CN 201580061211A CN 107110160 A CN107110160 A CN 107110160A
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- Prior art keywords
- flow path
- refrigerant flow
- refrigerant
- bent axle
- compression mechanism
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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
Abstract
Multi-cylinder hermetic type compressor includes the 1st silencer room, 2nd silencer room and a plurality of refrigerant flow path of the 1st silencer room of connection and the 2nd silencer room, 1st silencer room side of the 1st discharge port is provided with check-valves, the check-valves has needle spring plate valve construction, and there is fixing end at one end, 1st discharge port is in staggered configuration in the circumference centered on bent axle along a direction of rotation and fixing end, being configured on the direction of rotation in a plurality of refrigerant flow path has the sectional area less than other at least 1 article refrigerant flow path in the refrigerant flow path away from the farthest position of the 1st discharge port.
Description
Technical field
The present invention relates to a kind of multi-cylinder hermetic type compressor with multiple compression mechanisms.
Background technology
Hermetic type compressor includes the motor part of closed container (hereinafter referred to as " shell "), configuration in shell (hereinafter referred to as
" motor ") and the motor-driven compression unit of utilization.
In such hermetic type compressor, compressed via the refrigerant of suction pipe arrangement supply in compression unit, via disappearing
Sound device room is discharged in shell, is discharged to from discharge pipe outside shell.The hermetic type compressor is for example used in refrigerator, freezer, air-conditioning
With water heater etc., it requires high efficiency and cost degradation.
In addition, in the case of the single cylinder hermetic type compressor with single cylinder, compression unit is made up of single compression mechanism.
Compression mechanism includes：Circular cylinder body；Circular rotary piston, the circular rotary piston is configured in cylinder body
Inner peripheral portion simultaneously carries out eccentric rotary；Blade, blade configuration is being formed in the blade groove of cylinder body, is retreated certainly along the radial direction of cylinder body
Such as；Force application part (such as helical spring), the force application part pushes blade along the direction gone to the central shaft of cylinder body.In addition,
Compression mechanism also includes：Bent axle, the bent axle is formed with the eccentric axial portion for making rotary piston carry out eccentric rotary；A pair of end
Plate, a pair of end plate by crankshaft support to rotate freely, and by the two ends face closure of cylinder body.Also, by the inner peripheral surface of cylinder body,
The space that the outer peripheral face and a pair of end plate of rotary piston are surrounded, by the leaf free to advance or retreat of the rotary piston towards eccentric rotary
Piece is divided into two into a pair of rooms (hereinafter referred to as " discharge chambe ") that volume integral does not increase and decrease.That is, it is gradually increased in volume as making
The mechanism that the refrigerant that phase is attracted is compressed in the phase that volume is gradually reduced.
On the other hand, in the multi-cylinder hermetic type compressor with 2 cylinder bodies, compression unit have will substantially with above-mentioned list
The same compression mechanism of cylinder hermetic type compressor is configured to the structure of 2 layers (2 grades) across demarcation strip.With through these compression mechanisms
Mode be provided with and refrigerant is flowed to the opposing party from the silencer room (hereinafter referred to as " the 1st silencer room ") of side's compression mechanism
The refrigerant flow path of the silencer room (hereinafter referred to as " the 2nd silencer room ") of compression mechanism.
In the multi-cylinder hermetic type compressor, the refrigerant gas discharged from side's compression mechanism is temporarily discharged into ring-type
1st silencer room.Then, the refrigerant gas for being discharged into the 1st muffler chambers is eliminated the noise by refrigerant flow path the 2nd of ring-type
Device room is collaborated with the refrigerant gas discharged from the opposing party's compression mechanism, is discharged in shell.
In multi-cylinder hermetic type compressor, the refrigerant of the 1st silencer room is compressed and is discharged into side's compression mechanism
Gas, the 2nd muffler chambers of another compression mechanism are transported to by refrigerant flow path.Therefore, when refrigerant gas passes through
During refrigerant flow path, the pressure loss is produced.The refrigerant gas can be increased by pressure loss during refrigerant flow path by (1)
The flow diameter of big refrigerant flow path, (2) increase this 2 kinds of methods of stream quantity of refrigerant flow path to reduce.
But, no matter in any method of the above method (1) or the above method (2), it is required for having in compression unit
Refrigerant flow path is set in the space of limit.Therefore, the amplification of flow path area is limited, and stream can not effectively be set by existing
Problem.
For example it is proposed that making the demarcation strip of the refrigerant flow path of the mutual silencer room of connection compression mechanism pass through portion
Bore expansion is connected, the pressure fluctuation for making refrigerant gas using the intercommunicating pore after the expansion mitigates in the midway of refrigerant flow path
(referring for example to patent document 1).
In addition, it is thus proposed that be provided separately refrigerant flow path a plurality of, realizing the installation space of refrigerant flow path ensures
With the amplification of flow path area (referring for example to patent document 2).
Prior art literature
Patent document
Patent document 1：Japanese Unexamined Patent Publication 2013-019370 publications (claim 1, Fig. 1, Fig. 2)
Patent document 2：Japanese Unexamined Patent Publication 2013-204465 publications (Fig. 2, Fig. 3)
The content of the invention
The invention problem to be solved
But, in the technology described in patent document 1 and patent document 2, there is following (a) and (b) such
Problem.
(a) compression mechanism is configured with suction inlet, discharge port and makes bolt hole of fastening parts etc., so can not be effectively
Refrigerant flow path is set.Further, since setting suction inlet, discharge port and bolt hole, the intensity of constituent part is also restrained,
So refrigerant flow path can not be configured freely.
(b) with (a) the reasons why is identical, and increase stream quantity is also highly difficult.
The present invention is made to solve problem as described above, it is therefore intended that refrigerant can be prevented by obtaining one kind
The increase of crushing, improves the multi-cylinder hermetic type compressor of compressor efficiency.
Scheme for solving problem
The multi-cylinder hermetic type compressor of the present invention includes：Closed container；Compression unit, above-mentioned compression unit is housed in above-mentioned closed
In container, with the 1st compression mechanism and the 2nd compression mechanism；Driving force is delivered to above-mentioned compression unit by bent axle, above-mentioned bent axle；
1st silencer room of ring-type, the 1st silencer room of above-mentioned ring-type is configured on the shaft core direction of above-mentioned bent axle in above-mentioned compression unit
A side, the refrigerant that have compressed in above-mentioned 1st compression mechanism is discharged to the 1st silencer room via the 1st discharge port；
2nd silencer room of ring-type, the 2nd silencer room of above-mentioned ring-type is configured on above-mentioned shaft core direction in the another of above-mentioned compression unit
Side, the refrigerant that have compressed in above-mentioned 2nd compression mechanism is discharged to the 2nd silencer room via the 2nd discharge port；It is a plurality of
Refrigerant flow path, above-mentioned a plurality of refrigerant flow path makes above-mentioned 1st silencer room be connected with above-mentioned 2nd silencer room, will be above-mentioned
The refrigerant of 2nd muffler chambers is directed to above-mentioned 1st silencer room；Outlet, above-mentioned outlet is by above-mentioned 1st silencer room
Interior refrigerant is discharged to the space in above-mentioned closed container, and above-mentioned 1st compression mechanism and above-mentioned 2nd compression mechanism have respectively
Have：Cylinder body；Rotary piston, inner peripheral surface of the above-mentioned rotary piston along above-mentioned cylinder body carries out eccentric rotary；Blade, above-mentioned blade
Space between the outer peripheral face of the inner peripheral surface of above-mentioned cylinder body and above-mentioned rotary piston is separated；Blade groove, above-mentioned blade groove
Above-mentioned cylinder body is arranged at, above-mentioned blade is housed in the mode for making above-mentioned blade free to advance or retreat, above-mentioned a plurality of refrigerant flow path runs through
Set, the above-mentioned 1st of above-mentioned 1st discharge port the cylinder body of above-mentioned 1st compression mechanism and the cylinder body of above-mentioned 2nd compression mechanism
Silencer room side is provided with check-valves, and above-mentioned check-valves has needle spring plate valve construction, and has fixing end at one end, and above-mentioned the
1 discharge port is in staggered configuration in the circumference centered on above-mentioned bent axle along a direction of rotation with above-mentioned fixing end, above-mentioned a plurality of
Being configured on above-mentioned direction of rotation in the refrigerant flow path away from the farthest position of above-mentioned 1st discharge port in refrigerant flow path,
Sectional area with less than other at least 1 refrigerant flow path.
Invention effect
Using the present invention, the increase of the refrigerant crushing in multi-cylinder hermetic type compressor can be prevented, compressor effect is improved
Rate.
Brief description of the drawings
Fig. 1 is the sectional view of the integrally-built side view for the multi-cylinder hermetic type compressor for representing embodiments of the present invention 1.
Fig. 2 is the partial sectional view of the side view of the compression unit for the multi-cylinder hermetic type compressor for representing Fig. 1.
Fig. 3 is Fig. 1 A-A direction of arrow sectional views.
Fig. 4 is Fig. 1 B-B direction of arrow sectional views.
Fig. 5 is Fig. 4 C-C direction of arrow sectional views.
Fig. 6 is represented the multi-cylinder hermetic type compressor of embodiments of the present invention 1 applied to complete in the case of air-conditioning
The curve map of year running efficiency.
Fig. 7 is the discrepancy mouth-shaped of the refrigerant flow path for the multi-cylinder hermetic type compressor for representing embodiments of the present invention 2
The sectional view equivalent to Fig. 3.
Fig. 8 is Fig. 7 D-D direction of arrow sectional views.
Embodiment
Embodiment 1.
Hereinafter, embodiments of the present invention are illustrated.
Fig. 1 is the sectional view of the integrally-built side view for the multi-cylinder hermetic type compressor for representing embodiments of the present invention 1.
Fig. 2 is the partial sectional view of the side view of the compression unit for the multi-cylinder hermetic type compressor for representing Fig. 1.Fig. 3 is Fig. 1 A-A arrow sides
To sectional view.Fig. 4 is Fig. 1 B-B direction of arrow sectional views.In addition, each figure is schematically to describe above, so the present invention is simultaneously
It is not limited to embodiment illustrated.
As shown in Figure 1 to 4, the multi-cylinder hermetic type compressor 100 of present embodiment 1 includes the shell as closed container
101st, it is arranged on the motor part (hereinafter referred to as " motor ") 102 as driving source of the inside of shell 101 and is arranged on the shell 101
Inside compression unit 103.Hereinafter, the structure of each several part is further described.
Shell
Shell 101 has upper case 101a and central portion shell 101b.Alternatively, it is also possible to roughly the same with upper case 101a
The lower case of shape.It is provided with for the glass terminal 104 from outside to the supply electric power of motor 102, and uses in upper case 101a
Refrigerant after by compression is discharged to the shell 101 i.e. discharge pipe 105 of the outside of multi-cylinder hermetic type compressor 100.
Motor 102, the compressions of the 1st compression mechanism 10a for constituting compression unit 103 and the 2nd are fixed with central portion shell 101b
Mechanism 10b, one end respectively with the 1st compression mechanism 10a the 1st suction inlet 16a (reference picture 4) and the 2nd compression mechanism 10b
2 suction inlet 16b (reference picture 3) are connected and guided the 1st suction line 106a and the 2nd suction line 106b of refrigerant.1st suction
Pipe 106a and the 2nd respective other ends of suction line 106b are connected with suction silencer 107.In suction silencer 107, enter
The removal of rubbish in the gas-liquid separation of row refrigerant and refrigerant.
Motor
Motor 102 includes stator 102a and rotor 102b.Rotor 102b (is separately done in detail installed in bent axle 50 on the bent axle 50
Describe in detail bright) on.The torque that motor 102 is produced is delivered to the 1st compression mechanism 10a and the 2nd compression mechanism using bent axle 50
10b。
Compression unit
Compression unit 103 has following structure, i.e. by the 1st compression mechanism 10a and the 2nd compression mechanism 10b with across separation
The mode of plate 30 is laminated, and is matched somebody with somebody by the two ends of the component of above-mentioned 1st compression mechanism 10a and the 2nd compression mechanism 10b accumulations
It is equipped with the 1st end plate 20a and the 2nd end plate 20b of supporting bent axle 50.Also, above-mentioned 1st compression mechanism 10a, the 2nd compression mechanism
10b, demarcation strip 30, the 1st end plate 20a and the 2nd end plate 20b are as shown in Fig. 2 tight by length different two kinds of bolts 71a, 71b
It is solidified as a whole.
1st compression mechanism 10a possesses the 1st cylinder body 11a of annular shape, and inner peripheral portion and edge of the configuration in the 1st cylinder body 11a
1st cylinder body 11a inner peripheral surface carries out circular the 1st rotary piston (hereinafter referred to as " the 1st piston ") 12a of eccentric rotary.
In addition, the 1st compression mechanism 10a is also equipped with being formed at the 1st cylinder body 11a the 1st blade groove 13a, along the 1st in the 1st blade groove 13a
The 1st blade 14a that cylinder body 11a radial direction is movably configured, and the 1st blade 14a is pushed to the 1st piston 12a periphery
The 1st spring 15a.1st piston 12a outer peripheral face is abutted with the abutted position of wire with the 1st cylinder body 11a inner peripheral surface.With
1st piston 12a eccentric rotary, the abutted position of wire is along the circumferential direction moved.1st cylinder body 11a openend is by the 1st end plate
20a is closed.
Equally, the 2nd compression mechanism 10b possesses the 2nd cylinder body 11b of annular shape, and configuration in the 2nd cylinder body 11b inner peripheral portion
And circular the 2nd rotary piston (hereinafter referred to as " the 2nd work of eccentric rotary is carried out along the 2nd cylinder body 11b inner peripheral surface
Plug ") 12b.In addition, the 2nd compression mechanism 10b is also equipped with being formed at the 2nd cylinder body 11b the 2nd blade groove 13b, in the 2nd blade groove
The 2nd blade 14b movably configured along the 2nd cylinder body 11b radial direction in 13b, and by the 2nd blade 14b to the 2nd piston 12b
Periphery push the 2nd spring 15b.2nd piston 12b outer peripheral face is with the abutted position of wire and the 2nd cylinder body 11b inner peripheral surface
Abut.With the 2nd piston 12b eccentric rotary, the abutted position of wire is along the circumferential direction moved.2nd cylinder body 11b openend
By the 2nd end plate 20b closings.
In addition, the 1st cylinder body 11a internal diameter and the 2nd cylinder body 11b internal diameter are designed as equal.
Bent axle
Bent axle 50, which has, coaxially matches somebody with somebody the 1st bearing insertion section 52a, the bearing insertion section 52b of demarcation strip insertion section 53 and the 2nd
The structure put.It is formed between the 1st bearing insertion section 52a and demarcation strip insertion section 53 towards the 1st eccentric eccentric shaft of a side
Portion 51a.It is formed between the 2nd bearing insertion section 52b and demarcation strip insertion section 53 towards the 2nd eccentric eccentric axial portion of the opposing party
51b.1st eccentric axial portion 51a and the 2nd eccentric axial portion 51b is eccentric along the direction that mutual phase differs 180 °.1st eccentric axial portion
51a and the 2nd eccentric axial portion 51b each central shaft are parallel with the shaft core of bent axle 50.
In addition, the 1st bearing 25a supportings that the 1st bearing insertion section 52a is arranged on the 1st end plate 20a inner peripheral surface are rotation
Freely.2nd bearing 25b of the inner peripheral surface that the 2nd bearing insertion section 52b is arranged on the 2nd end plate 20b is rotatably supported.Point
The central center through hole 30a for being formed at demarcation strip 30 has been run through in dividing plate insertion section 53.
1st silencer room and the 2nd silencer room
As shown in figure 4, the 1st compression mechanism 10a the 1st end plate 20a be provided be connected with the 1st discharge chambe 40a the 1st
Discharge port 17a, and be made up of from the downstream that refrigerant flows with setting pressure by what the 1st discharge port 17a was closed leaf spring
The 1st check-valves 18a.In addition, the 1st lid 19a is chimeric with the 1st end plate 20a in the way of covering the 1st discharge port 17a.Also,
Utilize the 1st the 1st silencer room 60a of lid 19a and the 1st end plate 20a formation.1st silencer room 60a is formed as centered on bent axle 50
Ring-type, the 1st silencer room 60a configures the upper end side in compression unit 103 on the shaft core direction of bent axle 50.
Thus, compressed in the 1st compression mechanism 10a and reached the refrigerant of setting pressure and passed through the 1st discharge port 17a
It is discharged into the 1st silencer room 60a.
In the 1st lid 19a provided with 2 outlets 21a, 21b.Refrigerant in 1st silencer room 60a by outlet 21a,
21b is discharged into the space in shell 101.Here, using bent axle 50 (such as the shaft core of bent axle 50) as in the circumference at center, by leaf
Film trap 13a position is set to 0 °, and the counter clockwise direction (the overall flow direction of refrigerant described later) in Fig. 4 is set into square
To.Now, outlet 21a, which is arranged on, reaches (0 °≤the θ 1 of angle, θ 1<360 °) position, outlet 21b, which is arranged on, reaches angle, θ
2(θ1<θ2<360 °) position.In addition, outlet 21a, 21b circumferential position are according to the respective center of outlet 21a, 21b
Position is determined.In this example, outlet 21a, 21b is arranged on as to be mutually facing across bent axle 50.For example, angle, θ 1 is about
For 90 °, angle, θ 2 is about 270 °.
As shown in figure 3, the 2nd compression mechanism 10b the 2nd end plate 20b be provided be connected with the 2nd discharge chambe 40b the 2nd
Discharge port 17b, and be made up of from the downstream that refrigerant flows with setting pressure by what the 2nd discharge port 17b was closed leaf spring
The 2nd check-valves 18b.In addition, the 2nd lid 19b is chimeric with the 2nd end plate 20b in the way of covering the 2nd discharge port 17b.Also,
Utilize the 2nd the 2nd silencer room 60b of lid 19b and the 2nd end plate 20b formation.2nd silencer room 60b is formed as centered on bent axle 50
Ring-type, the 2nd silencer room 60b configures the lower end side in compression unit 103 on the shaft core direction of bent axle 50.
Fig. 5 is Fig. 4 C-C direction of arrow sectional views, represents the 1st check-valves 18a structure.As shown in figure 5, the 1st non-return
Valve 18a has the openend 17a2 for the 1st silencer room 60a sides that the 1st discharge port 17a is opened and closed according to the discharge pressure of refrigerant
Needle spring plate valve construction.1st check-valves 18a includes the valve element 81 of leaf-spring-like, and limits the valve guard 82 of the flexure of valve element 81.
The fixing end 81a positioned at one end of valve element 81 is fixed on the 1st end plate together with the one end of valve guard 82 by rivet 83
20a.When the pressure differential of the refrigerant pressure in the refrigerant pressure in the 1st discharge chambe 40a and the 1st silencer room 60a is smaller,
The other end side of valve element 81 is abutted with the 1st discharge port 17a openend 17a2.Thus, the 1st check-valves 18a, which turns into, closes
State.And when the pressure differential of the refrigerant pressure in the 1st discharge chambe 40a and the refrigerant pressure in the 1st silencer room 60a increases
When, as shown in the double dot dash line in Fig. 5, the other end side (free end side) of valve element 81 leaves the 1st because of the flexure of valve element 81
Discharge port 17a openend 17a2.Thus, the 1st check-valves 18a turns into the refrigerant in open mode, the 1st discharge chambe 40a
It is discharged to via the 1st discharge port 17a in the 1st silencer room 60a.Valve element 81 now is with more remote apart from fixing end 81a, with opening
Separately bigger mode is tilted relative to the 1st discharge port 17a by mouthful end 17a2.Thus, flow into the 1st from the 1st discharge port 17a and disappear
Refrigerant in sound device room 60a is guided as shown in the block arrow in Fig. 5 by valve element 81 along the direction for leaving fixing end 81a.
As shown in figure 4, the 1st check-valves 18a fixing end 81a and the 1st discharge port 17a are in the ring centered on bent axle 50
In 1st silencer room 60a of shape, configure in the position circumferentially staggered.Thus, the refrigerant in the 1st silencer room 60a is produced
The overall circumferential flowing gone along a side direction of rotation.In Fig. 4, the 1st discharge port 17a is arranged in the counterclockwise direction with consolidating
The position that fixed end 81a staggers.Therefore, in Fig. 4, the overall flow direction of the refrigerant in the 1st silencer room 60a is the inverse time
Pin direction.
2nd check-valves 18b is same with the 1st check-valves 18a, including valve element 81, valve guard 82 and rivet 83, and with
1 check-valves 18a is configured symmetrical above and belowly.Thus, according to the reasons why as described above, the refrigerant production in the 2nd silencer room 60b
The raw overall circumferential flowing gone along a side direction of rotation.In figure 3, the 2nd discharge port 17b be arranged on along clockwise direction with
The position that 2nd check-valves 18b fixing end 81a staggers.Therefore, in figure 3, the entirety of the refrigerant in the 2nd silencer room 60b
Flow direction for clockwise.
Refrigerant flow path
At least by 1 article of (being in this example 3 articles) cold-producing medium stream between 1st silencer room 60a and the 2nd silencer room 60b
Road 33a, 33b, 33c connection.In Fig. 1, as refrigerant flow path 33,1 refrigerant flow path is only represented.Refrigerant flow path 33a,
33b, 33c are for example with circular cross sectional shape.Be discharged into the 2nd silencer room 60b refrigerant via refrigerant flow path 33a,
33b, 33c are directed into the 1st silencer room 60a.Refrigerant flow path 33a, 33b, 33c and the 1st discharge chambe 40a and the 2nd compression
Room 40b adjoining configurations.Refrigerant flow path 33a, 33b, 33c extend along the direction parallel with bent axle 50.Refrigerant flow path 33a,
33b, 33c are with through the 1st end plate 20a, the 1st compression mechanism 10a the 1st cylinder body 11a, demarcation strip 30, the 2nd compression mechanism 10b
2nd cylinder body 11b and the 2nd end plate 20b mode is formed.
Refrigerant flow path 33a, 33b, 33c are along with bent axle 50 around the 1st discharge chambe 40a and the 2nd discharge chambe 40b
The circumferential array at center.When in the circumference centered on bent axle 50, when blade groove 13a, 13b position are set into 0 °, from pressure
Contracting portion 103 axis direction (lower face side) observation, refrigerant flow path 33a, 33b, 33c along clockwise direction (or counterclockwise side
To) be only formed in the range of 90 °~270 °.In addition, when in the circumference centered on bent axle 50, by blade groove 13a, 13b
Position be set to 0 °, and when the counter clockwise direction (the overall flow direction of refrigerant) in Fig. 4 is set into positive direction, refrigerant
Stream 33a, 33b, 33c are only formed in 1~θ of θ 2 angular range.In addition, refrigerant flow path 33a, 33b, 33c's is circumferential
Position is determined by the respective center of refrigerant flow path 33a, 33b, 33c.
As described above, the overall flow direction of the refrigerant of the construction based on check-valves 18a, 18b, shown in Fig. 3
It is clockwise direction in 2nd silencer room 60b, for counterclockwise in the 1st silencer room 60a shown in Fig. 4.Cold-producing medium stream
Refrigerant flow path 33c in road 33a, 33b, 33c is in the overall flowing side of the refrigerant of the construction based on check-valves 18a, 18b
Upwards, configuration is in the position farthest away from discharge port 17a, 17b.In other words, the refrigerant in refrigerant flow path 33a, 33b, 33c
Stream 33c is configured in the position nearest away from discharge port 17a, 17b on the direction opposite with above-mentioned flow direction.Refrigerant
Stream 33c has the sectional area less than other refrigerant flow paths 33a, 33b.In this example, refrigerant flow path 33a, 33b, 33c is equal
With circular cross sectional shape, so refrigerant flow path 33c is formed as than refrigerant flow path 33a, 33b paths.In this example, make
Refrigerant line 33a, 33b have identical sectional area, but away from discharge port 17a, 17b on the overall flow direction of refrigerant
Nearest refrigerant flow path 33a, it is possible to have more than refrigerant flow path 33b sectional area.I.e., it is possible to be, in refrigerant
On overall flow direction, away from the refrigerant flow path that discharge port 17a, 17b is nearer, just there is bigger sectional area.In addition, system
The sectional area of refrigerant line is to make axially penetrating through for cold-producing medium stream curb bent axle 50, the cold-producing medium stream with this on axially vertical face
The area on road.
In Fig. 4, the overall flow direction of the refrigerant of the construction based on check-valves 18a, 18b is counter clockwise direction,
So the refrigerant in the 1st silencer room 60a is discharged into from refrigerant flow path 33a and discharge port 17a, mainly from outlet
21a is discharged to the space in shell 101.The refrigerant being discharged into from refrigerant flow path 33b, 33c in the 1st silencer room 60a is main
The space in shell 101 is discharged to from outlet 21b.But it is discharged into the refrigeration in the 1st silencer room 60a from refrigerant flow path 33b
A part for agent flows along the direction opposite with overall flow direction, from outlet 21a discharges.
Discharge capacity
Refrigerant flow path 33a, 33b, 33c sectional area summation are being set to S [mm2], by the every of the 2nd compression mechanism 10b
Turn 1 (Japanese：1 time translocation works as り) discharge capacity be set to Vst [cc] in the case of, total sectional area S and discharge capacity Vst are for example set
To meet 11 [mm2/cc]≤S/Vst≤20[mm2/ cc] relation.Its reason is seen below.
The compression of refrigerant
As shown in Figure 1 and Figure 2, the 1st eccentric axial portion 51a runs through the 1st piston 12a inner peripheral portion, the 2nd eccentric axial portion 51b
Through the 2nd piston 12b inner peripheral portion.Therefore, with the rotation of bent axle 50, the 1st piston 12a and the 2nd piston 12b with a side with
The state that the opposing party differs 180 ° of phases carries out eccentric rotary.
The 1st piston 12a and the 1st blade 14a free to advance or retreat of eccentric rotary are carried out using the rotation with bent axle 50
The volume of the side room for the 1st discharge chambe 40a being divided into two gradually increases.In addition, the 1st discharge chambe 40a being divided into two
The volume of the opposing party room is correspondingly gradually reduced.Also, it is formed with the 1st in the position of the side room equivalent to the 1st discharge chambe 40a
Suction inlet 16a, the 1st discharge port 17a (reference picture 4) is formed with the position of the opposing party room equivalent to the 1st discharge chambe 40a.
That is, the 1st suction inlet 16a and the 1st discharge port 17a matches somebody with somebody from the axis direction of bent axle 50 on the direction of rotation of bent axle 50
It is set to across the 1st blade 14a.That is, after refrigerant has been sucked from the 1st suction inlet 16a, by the refrigerant compression from
1st discharge port 17a is discharged in the 1st silencer room 60a.
In addition, carrying out the 2nd piston 12b and the 2nd leaf free to advance or retreat of eccentric rotary using the rotation with bent axle 50
The volume of the side room for the 2nd discharge chambe 40b that piece 14b is divided into two gradually increases.In addition, the 2nd discharge chambe being divided into two
The volume of 40b the opposing party room is correspondingly gradually reduced.Also, formed in the position of the side room equivalent to the 2nd discharge chambe 40b
There is the 2nd suction inlet 16b, the 2nd discharge port 17b (references are formed with the position of the opposing party room equivalent to the 2nd discharge chambe 40b
Fig. 3).That is, the 2nd suction inlet 16b and the 2nd discharge port 17b from the axis direction of bent axle 50 in the direction of rotation of bent axle 50
On be configured to across the 2nd blade 14b.That is, after refrigerant has been sucked from the 2nd suction inlet 16b, by the refrigerant compression
And be discharged to from the 2nd discharge port 17b in the 2nd silencer room 60b.Also, it is discharged to the refrigerant in the 2nd silencer room 60b
It is discharged to via a plurality of refrigerant flow path 33a, 33b, 33c in the 1st silencer room 60a.
Refrigerant in the 1st silencer room 60a is discharged to via refrigerant flow path 33a, 33b, 33c and from discharge port
17a is discharged into the refrigerant in the 1st silencer room 60a, is discharged to from the 1st lid 19a outlet 21a, 21b in shell 101.In detail
For, it is discharged into a part for the refrigerant in the 1st silencer room 60a from refrigerant flow path 33b and is arranged from refrigerant flow path 33a
The refrigerant being put into the 1st silencer room 60a does not reach discharge port 17a but given off from outlet 21a.From cold-producing medium stream
The remainder for the refrigerant that road 33b is discharged into the 1st silencer room 60a and it is discharged into the 1st silencer from refrigerant flow path 33c
Refrigerant in the 60a of room does not reach discharge port 17a but given off from outlet 21b.In addition, being discharged from discharge port 17a
The refrigerant gone out gives off not via refrigerant flow path 33a, 33b, 33c but from outlet 21a.
That is, refrigerant flow path 33a, 33b, 33c, discharge port 17a and outlet 21a, 21b are configured to not make from refrigeration
The refrigerant that agent stream 33a, 33b, 33c give off reaches discharge port 17a, and does not make what is given off from discharge port 17a
Refrigerant reaches refrigerant flow path 33a, 33b, 33c.Thus, the refrigerant being discharged into the 1st silencer room 60a will not be inhaled into
Adverse current occurs in refrigerant flow path 33a, 33b, 33c or discharge port 17a.
Fig. 6 is to represent the whole year in the case that the multi-cylinder hermetic type compressor 100 of present embodiment 1 is applied in air-conditioning
The curve map of running efficiency (APF).In figure 6, refrigerant flow path 33a, 33b, 33c total sectional area S and the 2nd compressor are represented
The ratio between structure 10b discharge capacity Vst S/Vst and the relation of annual running efficiency.Transverse axis represents S/Vst [mm2/ cc], the longitudinal axis represents complete
Year running efficiency.
In addition, the multi-cylinder hermetic type compressor 100 shown in Fig. 1 is the multi-cylinder hermetic type compressor of internal high pressure type.In addition,
In figure 6, using S/Vst as 8.9mm2On the basis of the annual running efficiency of/cc conventional multi-cylinder hermetic type compressor
(100%) the annual running efficiency of the multi-cylinder hermetic type compressor 100 of present embodiment 1, is represented.
As shown in fig. 6, when S/Vst is 11.2mm2During/cc, the annual running efficiency of multi-cylinder hermetic type compressor 100 is most
It is big more than 100.5%, when S/Vst is more than 8.9mm2/ cc and less than 24mm2During/cc, the whole year of multi-cylinder hermetic type compressor 100
Running efficiency is more than 100%.That is, by refrigerant flow path 33a, 33b, 33c total sectional area S and the 2nd compression mechanism 10b discharge capacity
Vst is set as the [mm of satisfaction 8.92/cc]<S/Vst<24[mm2/ cc] relation, so as to than conventional multi-cylinder hermetic type compressor
Improve annual running efficiency.In addition, manufacture deviation etc. is estimated in the product, to meet 11 [mm2/cc]≤S/Vst≤20[mm2/
Cc] the mode of relation set total sectional area S and discharge capacity Vst.
It can be seen from result more than, by the total sectional area S and the 2nd compressor that make refrigerant flow path 33a, 33b, 33c
The ratio between structure 10b discharge capacity Vst (S/Vst) reaches most preferably, can suppress refrigerant importeding into silencer room (this collaborated
In be the 1st silencer room 60a) when the pressure loss, improve annual running efficiency.
Thus, in the multi-cylinder hermetic type compressor 100 of present embodiment 1, for in the 2nd compression mechanism 10b quilts
Compress and be discharged into from the 2nd silencer room 60b via refrigerant flow path 33a, 33b, 33c the 1st silencer room 60a refrigerant
Pressure oscillation and the pulsation occurred, can effectively be subtracted using the 2nd silencer room 60b and refrigerant flow path 33a, 33b, 33c
Few above-mentioned pulsation.Also, the flowing of refrigerant can be directed to the 1st compressor in the state of the increase of the pressure loss is inhibited
Structure 10a the 1st silencer room 60a.Therefore, it is possible to improve compressor efficiency (COP).
In addition, by making refrigerant flow path 33a, 33b, 33c total sectional area S-phase as described above for the 2nd compressor
Structure 10b discharge capacity Vst reaches most preferably, can reduce the pressure loss.In addition, as shown in figure 4, when in the week centered on bent axle 50
Upwards, blade groove 13a position is set to 0 °, when counter clockwise direction is set into positive direction, the 1st lid 19a outlet 21a configurations
Position near 90 °, outlet 21b configures the position near 270 °.By being configured so that, it can make from the 1st discharge port
17a is discharged to the refrigerant in the 1st silencer room 60a, with from the 2nd silencer room 60b via refrigerant flow path 33a, 33b, 33c
The refrigerant being flowed into the 1st silencer room 60a is efficiently separated.Thus, energy will be from the 1st silencer room 60a to the 2nd silencer
Room 60b adverse current and adverse current from the 1st from silencer room 60a to the 1st compression mechanism 10a the 1st discharge chambe 40a are suppressed to minimum
Degree.Thereby, it is possible to fully play the total sectional area S and the 2nd compression mechanism 10b that make refrigerant flow path 33a, 33b, 33c
The effect that the ratio between discharge capacity Vst (S/Vst) is obtained after reaching most preferably.
In addition, refrigerant flow path 33a, 33b, 33c as discussed previously with respect to blade groove 13a, 13b along clockwise direction (or
Counterclockwise) it is only formed in the range of 90 °~270 °.In addition, in the refrigerant of construction based on check-valves 18a, 18b
On overall flow direction, have from refrigerant flow path 33c of discharge port 17a, the 17b observation configuration in farthest position and be less than
Other refrigerant flow paths 33a, 33b sectional area.From refrigerant flow path 33c observations, the overall flow direction of refrigerant
Distance with discharge port 17a is nearer than refrigerant flow path 33a, 33b, so being discharged into the 1st silencer room from refrigerant flow path 33c
Refrigerant in 60a may be inhaled into discharge port 17a in the case of not from outlet 21b discharges.When from cold-producing medium stream
When the refrigerant that road 33c is discharged into the 1st silencer room 60a is inhaled into discharge port 17a, pressure loss increase.But,
In present embodiment 1, refrigerant flow path 33c has the sectional area less than other refrigerant flow paths 33a, 33b, so can subtract
The flow of few refrigerant being discharged into from refrigerant flow path 33c in the 1st silencer room 60a.Thus, it is possible to suppress from cold-producing medium stream
The refrigerant that road 33c is discharged into the 1st silencer room 60a is inhaled into discharge port 17a.On the other hand, refrigerant flow path
33a, 33b have the sectional area more than refrigerant flow path 33c, are eliminated the noise so can also reduce from the 2nd silencer room 60b to the 1st
The device room 60a pressure loss.Accordingly, it is capable to which the flowing of refrigerant is directed into the state of the increase of the pressure loss is inhibited
1 compression mechanism 10a the 1st silencer room 60a, can improve compressor efficiency.
In addition, when assume relative to blade groove 13a, 13b along clockwise direction (or counterclockwise) at 0 °~90 ° and
In the case of forming refrigerant flow path 33a, 33b, 33c in the range of 270 °~360 °, discharge port is configured with the range
17a, 17b, suction inlet 16a, 16b and blade groove 13a, 13b etc., thus can not configure freely refrigerant flow path 33a, 33b,
33c.In addition, when on the basis of the hollow construction such as discharge port 17a, 17b, suction inlet 16a, 16b and blade groove 13a, 13b
On, when intensively setting hollow refrigerant flow path 33a, 33b, 33c, cylinder body 11a, 11b intensity decline, and easily occur shape
Deformation.
In this regard, in present embodiment 1, relative to blade groove 13a, 13b, (or counter clockwise direction) exists along clockwise direction
Refrigerant flow path 33a, 33b, 33c are formed with the range of 90 °~270 °, so cylinder body 11a, 11b intensity can be suppressed
Decline.Even if refrigerant flow path 33a, 33b, 33c are configured in the range of 90 °~270 ° relative to blade groove 13a, 13b,
Can be by setting outlet 21a, 21b respectively near 90 ° and 270 ° relative to blade groove 13a, 13b, and will freeze certainly
The refrigerant that agent stream 33a, 33b, 33c give off is discharged in shell 101 from outlet 21a, 21b.Thereby, it is possible to suppress to be arranged
The refrigerant for being put into the 1st silencer room 60a is sucked again to refrigerant flow path 33a, 33b, 33c, or is inhaled into discharge
Port 17a.
Embodiment 2.
Fig. 7 is the discrepancy mouth-shaped of the refrigerant flow path for the multi-cylinder hermetic type compressor for representing embodiments of the present invention 2
The sectional view equivalent to Fig. 3.Fig. 8 is Fig. 7 D-D direction of arrow sectional views, represents the 2nd end plate 20b structure.In addition,
In figure, for the above-mentioned identical funtion part of embodiment 1, mark with the above-mentioned identical reference of embodiment 1.Separately
Outside, in explanation, with reference to above-mentioned Fig. 1 and Fig. 2.
In the multi-cylinder hermetic type compressor 100 of present embodiment 2, as shown in Figure 7 and Figure 8, in each refrigerant flow path
33a, 33b, 33c inflow entrance and flow export are provided with opening portion (can be taper or chamfering) 33d, 33e, 33f, above-mentioned to open
Oral area 33d, 33e, 33f have the sectional area of the sectional area more than above-mentioned refrigerant flow path 33a, 33b, 33c.
In the multi-cylinder hermetic type compressor 100 of present embodiment 2, in each refrigerant flow path 33a, 33b, 33c inflow
Mouth and flow export are provided with opening portion 33d, 33e, 33f, and above-mentioned opening portion 33d, 33e, 33f, which have, is more than above-mentioned cold-producing medium stream
The sectional area of road 33a, 33b, 33c sectional area, so the flowing of the refrigerant in refrigerant flow path 33a, 33b, 33c is smooth,
Result in the effect of the further reduction pressure loss.
As described above, the multi-cylinder hermetic type compressor 100 of above-mentioned embodiment 1 and embodiment 2 includes：Shell 101；Pressure
Contracting portion 103, above-mentioned compression unit 103 is housed in shell 101, with the 1st compression mechanism 10a and the 2nd compression mechanism 10b；Bent axle
50, driving force is delivered to compression unit 103 by above-mentioned bent axle 50；1st silencer room 60a of ring-type, the 1st silencer of above-mentioned ring-type
Room 60a is configured on the shaft core direction of bent axle 50 in a side of compression unit 103, the system that have compressed using the 1st compression mechanism 10a
Cryogen is discharged to the 1st silencer room 60a via the 1st discharge port 17a；2nd silencer room 60b of ring-type, above-mentioned ring-type
2nd silencer room 60b configures the another side in compression unit 103 on above-mentioned shaft core direction, is pressed using the 2nd compression mechanism 10b
The refrigerant contracted is discharged to the 2nd silencer room 60b via the 2nd discharge port 17b；A plurality of refrigerant flow path 33a, 33b, 33c,
Above-mentioned a plurality of refrigerant flow path 33a, 33b, 33c make the 1st silencer room 60a be connected with the 2nd silencer room 60b, and the 2nd is eliminated the noise
Refrigerant in the 60b of device room is directed to the 1st silencer room 60a；Outlet 21a, 21b, above-mentioned outlet 21a, 21b disappear the 1st
Refrigerant in sound device room 60a is discharged to the space in shell 101, and the 1st compression mechanism 10a includes：1st cylinder body 11a；1st revolution
The inner peripheral surface of formula piston 12a, above-mentioned 1st rotary piston 12a along the 1st cylinder body 11a carries out eccentric rotary；1st blade 14a, on
The 1st blade 14a is stated to separate the space between the 1st cylinder body 11a inner peripheral surface and the 1st rotary piston 12a outer peripheral face；The
1 blade groove 13a, above-mentioned 1st blade groove 13a is arranged at the 1st cylinder body 11a, and the 1st blade 14a is housed as free to advance or retreat, the 2nd pressure
Contracting mechanism 10b includes：2nd cylinder body 11b；2nd rotary piston 12b, above-mentioned 2nd rotary piston 12b is along the 2nd cylinder body 11b's
Inner peripheral surface carries out eccentric rotary；2nd blade 14b, above-mentioned 2nd blade 14b live the 2nd cylinder body 11b inner peripheral surface and the 2nd swinging
The space filled between 12b outer peripheral face is separated；2nd blade groove 13b, above-mentioned 2nd blade groove 13b is arranged at the 2nd cylinder body 11b,
It is free to advance or retreat that 2nd blade 14b, which is housed, and a plurality of refrigerant flow path 33a, 33b, 33c run through the 1st cylinder body 11a and the 2nd cylinder body
Set 11b, check-valves 18a is provided with the 1st discharge port 17a the 1st silencer room 60a sides, above-mentioned check-valves 18a has
Needle spring plate valve is constructed, and has fixing end 81a at one end, and the 1st discharge port 17a is in the circumference centered on bent axle 50 along one
Square direction of rotation (being counterclockwise in Fig. 4) is in staggered configuration, a plurality of refrigerant flow path 33a, 33b, 33c with fixing end 81a
In configured on above-mentioned direction of rotation in the refrigerant flow path 33c away from position farthest the 1st discharge port 17a, with less than
Other at least 1 refrigerant flow path 33a, 33b sectional area.
Using the structure, it can suppress to be inhaled from the refrigerant that refrigerant flow path 33c is discharged into the 1st silencer room 60a
Enter to discharge port 17a, so the increase of the refrigerant crushing in multi-cylinder hermetic type compressor 100 can be prevented, improve compression
Engine efficiency.
In the multi-cylinder hermetic type compressor 100 of above-mentioned embodiment 1 and embodiment 2, when in being with bent axle 50
In the circumference of the heart, the 1st blade groove 13a position is set to 0 °, when above-mentioned direction of rotation is set into positive direction, a plurality of cold-producing medium stream
Road 33a, 33b, 33c can be in the angular ranges for being circumferentially arranged at 90 °~270 ° centered on bent axle 50 (such as only at this
Angular range) in.
Using the structure, cold-producing medium stream is set with can suppressing the decline of the 1st cylinder body 11a and the 2nd cylinder body 11b intensity
Road 33a, 33b, 33c.
In the multi-cylinder hermetic type compressor 100 of above-mentioned embodiment 1 and embodiment 2, outlet includes the 1st discharge
Mouth 21a and the 2nd outlet 21b, will when in the circumference centered on bent axle 50, the 1st blade groove 13a position is set into 0 °
Above-mentioned direction of rotation is set to positive direction, and angle, θ 1 and angle, θ 2 are set into 0 °≤θ 1<θ2<At 360 °, the 1st outlet 21a exists
Being circumferentially arranged at centered on bent axle 50 reaches the position of angle, θ 1, and the 2nd outlet 21b is in the week centered on bent axle 50
Set up and reaching the position of angle, θ 2, a plurality of refrigerant flow path 33a, 33b, 33c can also be centered on bent axles 50
It is circumferentially arranged in the angular range (such as only in the angular range) for reaching 1~θ of θ 2.
Using the structure, the refrigerant being discharged into from refrigerant flow path 33a, 33b, 33c in the 1st silencer room 60a can be made
Discharge not via the 1st discharge port 17a but from outlet 21a, 21b.Therefore, it is possible to suppress from refrigerant flow path 33a, 33b,
The refrigerant that 33c is discharged into the 1st silencer room 60a is inhaled into the 1st discharge port 17a.
, can be in a plurality of refrigerant in the multi-cylinder hermetic type compressor 100 of above-mentioned embodiment 1 and embodiment 2
The respective inflow entrance of stream 33a, 33b, 33c and flow export are provided with opening portion 33d, 33e, 33f, above-mentioned opening portion 33d,
33e, 33f have the sectional area more than a plurality of respective sectional area of refrigerant flow path 33a, 33b, 33c.
Using the structure, the flowing of the refrigerant at refrigerant flow path 33a, 33b, 33c smoothly, is resulted in further
Reduce the effect of the pressure loss.
In addition, the multi-cylinder hermetic type compressor 100 of above-mentioned embodiment 1 and embodiment 2 includes：Shell 101；Compression unit
103, above-mentioned compression unit 103 is housed in shell 101, with the 1st compression mechanism 10a and the 2nd compression mechanism 10b；Bent axle 50, on
State bent axle 50 and driving force is delivered to compression unit 103；1st silencer room 60a of ring-type, the 1st silencer room 60a of above-mentioned ring-type
Configured on the shaft core direction of bent axle 50 in a side of compression unit 103, the refrigerant that have compressed using the 1st compression mechanism 10a
The 1st silencer room 60a is discharged to via the 1st discharge port 17a；2nd silencer room 60b of ring-type, the 2nd of above-mentioned ring-type eliminates the noise
Device room 60b configures the another side in compression unit 103 on above-mentioned shaft core direction, the system that have compressed using the 2nd compression mechanism 10b
Cryogen is discharged to the 2nd silencer room 60b via the 2nd discharge port 17b；At least 1 refrigerant flow path 33a, 33b, 33c, it is above-mentioned
At least 1 article refrigerant flow path 33a, 33b, 33c make the 1st silencer room 60a be connected with the 2nd silencer room 60b, and the 2nd is eliminated the noise
Refrigerant in the 60b of device room is directed to the 1st silencer room 60a；Outlet 21a, 21b, above-mentioned outlet 21a, 21b disappear the 1st
Refrigerant in sound device room 60a is discharged to the space in shell 101, and the 1st compression mechanism 10a includes：1st cylinder body 11a；1st revolution
The inner peripheral surface of formula piston 12a, above-mentioned 1st rotary piston 12a along the 1st cylinder body 11a carries out eccentric rotary；1st blade 14a, on
The 1st blade 14a is stated to separate the space between the 1st cylinder body 11a inner peripheral surface and the 1st rotary piston 12a outer peripheral face；The
1 blade groove 13a, above-mentioned 1st blade groove 13a is arranged at the 1st cylinder body 11a, and the 1st blade 14a is housed as free to advance or retreat, the 2nd pressure
Contracting mechanism 10b includes：2nd cylinder body 11b；2nd rotary piston 12b, above-mentioned 2nd rotary piston 12b is along the 2nd cylinder body 11b's
Inner peripheral surface carries out eccentric rotary；2nd blade 14b, above-mentioned 2nd blade 14b live the 2nd cylinder body 11b inner peripheral surface and the 2nd swinging
The space filled between 12b outer peripheral face is separated；2nd blade groove 13b, above-mentioned 2nd blade groove 13b is arranged at the 2nd cylinder body 11b,
It is free to advance or retreat that 2nd blade 14b, which is housed, and at least 1 article refrigerant flow path 33a, 33b, 33c run through the 1st cylinder body 11a and the 2nd cylinder
Set, at least 1 refrigerant flow path 33a, 33b, 33c total sectional area S [mm body 11b2] with the 2nd compression mechanism 10b's
Every turn 1 time discharge capacity Vst [cc] meet 8.9 [mm2/cc]<S/Vst<24[mm2/ cc] relation.
Using the structure, the discharge capacity Vst according to the 2nd compression mechanism 10b makes refrigerant flow path 33a, 33b, 33c total cross section
Product S is optimized, so the increase of the refrigerant crushing in multi-cylinder hermetic type compressor 100 can be prevented, improves compressor efficiency.
, can be in the 1st discharge port in the multi-cylinder hermetic type compressor 100 of above-mentioned embodiment 1 and embodiment 2
17a the 1st silencer room 60a sides are provided with the 1st check-valves 18a, and there is above-mentioned 1st check-valves 18a needle spring plate valve to construct, and
One end has fixing end 81a, and the 1st discharge port 17a is in the circumference centered on bent axle 50 along a side direction of rotation (in Fig. 4
In for counterclockwise) be in staggered configuration with fixing end 81a, when in the circumference centered on bent axle 50, by the 1st blade groove 13a
Position be set to 0 °, when above-mentioned direction of rotation is set into positive direction, at least 1 refrigerant flow path 33a, 33b, 33c are with bent axle
The angular range (such as only in the angular range) for being circumferentially arranged at 90 °~270 ° centered on 50.
Using the structure, cold-producing medium stream is set with can suppressing the decline of the 1st cylinder body 11a and the 2nd cylinder body 11b intensity
Road 33a, 33b, 33c.
, can be in the 1st discharge port in the multi-cylinder hermetic type compressor 100 of above-mentioned embodiment 1 and embodiment 2
17a the 1st silencer room 60a sides are provided with the 1st check-valves 18a, and there is above-mentioned 1st check-valves 18a needle spring plate valve to construct, and
One end has fixing end 81a, and the 1st discharge port 17a is in the circumference centered on bent axle 50 along a side direction of rotation (in Fig. 4
In for counterclockwise) be in staggered configuration with fixing end 81a, outlet include the 1st outlet 21a and the 2nd outlet 21b, when
In circumference centered on bent axle 50, the 1st blade groove 13a position is set to 0 °, above-mentioned direction of rotation is set to positive direction, will
Angle, θ 1 and angle, θ 2 are set to 0 °≤θ 1<θ2<At 360 °, the 1st outlet 21a is set up in the week centered on bent axle 50
The position of angle, θ 1 is being reached, the 2nd outlet 21b reaches the position of angle, θ 2 in being circumferentially arranged at centered on bent axle,
At least 1 refrigerant flow path 33a, 33b, 33c are in the angular range (example for being circumferentially arranged at 1~θ of θ 2 centered on bent axle 50
As only in the angular range).
Using the structure, the refrigerant being discharged into from refrigerant flow path 33a, 33b, 33c in the 1st silencer room 60a can be made
Discharge not via the 1st discharge port 17a but from outlet 21a, 21b.Therefore, it is possible to suppress from refrigerant flow path 33a, 33b,
The refrigerant that 33c is discharged into the 1st silencer room 60a is inhaled into the 1st discharge port 17a.
, can be at least 1 refrigeration in the multi-cylinder hermetic type compressor 100 of above-mentioned embodiment 1 and embodiment 2
Agent stream 33a, 33b, 33c inflow entrance and flow export are provided with opening portion 33d, 33e, 33f, above-mentioned opening portion 33d, 33e,
33f has the sectional area for the sectional area for being more than at least 1 refrigerant flow path 33a, 33b, 33c.
Using the structure, the flowing of the refrigerant in refrigerant flow path 33a, 33b, 33c smoothly, is resulted in further
Reduce the effect of the pressure loss.
Other embodiment
The present invention is not limited to above-mentioned embodiment, can carry out various modifications.
For example in the above-described embodiment, exemplified with the structure for being provided with 3 refrigerant flow paths 33a, 33b, 33c, but system
The number of refrigerant line can also be 1,2 or more than 4.
In addition, in the above-described embodiment, exemplified with the refrigerant flow path 33a with circular cross sectional shape, 33b,
33c, but refrigerant flow path can also have other cross sectional shapes such as rectangle.In addition, refrigerant flow path can also be along cylinder body
The elongated hole that extends in circular arc of circumference.
Description of reference numerals
10a, the 1st compression mechanism；10b, the 2nd compression mechanism；11a, the 1st cylinder body；11b, the 2nd cylinder body；12a, the 1st piston
(the 1st rotary piston)；12b, the 2nd piston (the 2nd rotary piston)；13a, the 1st blade groove；13b, the 2nd blade groove；14a,
1 blade；14b, the 2nd blade；15a, the 1st spring；15b, the 2nd spring；16a, the 1st suction inlet；16b, the 2nd suction inlet；17a, the 1st
Discharge port；17a2, openend；17b, the 2nd discharge port；18a, the 1st check-valves；18b, the 2nd check-valves；19a, the 1st lid；
19b, the 2nd lid；20a, the 1st end plate；20b, the 2nd end plate；21a, 21b, outlet；25a, the 1st bearing；25b, the 2nd bearing；30、
Demarcation strip；30a, center through hole；33rd, 33a, 33b, 33c, refrigerant flow path；33d, 33e, 33f, opening portion；40a, the 1st compression
Room；40b, the 2nd discharge chambe；50th, bent axle；51a, the 1st eccentric axial portion；51b, the 2nd eccentric axial portion；52a, the 1st bearing insertion section；
52b, the 2nd bearing insertion section；53rd, demarcation strip insertion section；60a, the 1st silencer room；60b, the 2nd silencer room；71a, 71b, spiral shell
Bolt；81st, valve element；81a, fixing end；82nd, valve guard；83rd, rivet；100th, multi-cylinder hermetic type compressor；101st, shell (closed appearance
Device)；101a, upper case；101b, central portion shell；102nd, motor (motor part)；102a, stator；102b, rotor；103rd, compress
Portion；104th, glass terminal；105th, discharge pipe；106a, the 1st suction line；106b, the 2nd suction line；107th, suction silencer.
Claims (8)
1. a kind of multi-cylinder hermetic type compressor, wherein,
The multi-cylinder hermetic type compressor includes：
Closed container；
Compression unit, the compression unit is housed in the closed container, with the 1st compression mechanism and the 2nd compression mechanism；
Driving force is delivered to the compression unit by bent axle, the bent axle；
1st silencer room of ring-type, the 1st silencer room of the ring-type is configured on the shaft core direction of the bent axle in the pressure
One side in contracting portion, the refrigerant that have compressed in the 1st compression mechanism is discharged to the 1st silencer via the 1st discharge port
Room；
2nd silencer room of ring-type, the 2nd silencer room of the ring-type is configured on the shaft core direction in the compression unit
Another side, the refrigerant that have compressed in the 2nd compression mechanism is discharged to the 2nd silencer room via the 2nd discharge port；
A plurality of refrigerant flow path, a plurality of refrigerant flow path makes the 1st silencer room be connected with the 2nd silencer room
It is logical, the refrigerant of the 2nd muffler chambers is directed to the 1st silencer room；
The refrigerant of 1st muffler chambers is discharged to the space in the closed container by outlet, the outlet,
1st compression mechanism and the 2nd compression mechanism have respectively：
Cylinder body；
Rotary piston, inner peripheral surface of the rotary piston along the cylinder body carries out eccentric rotary；
Blade, the blade separates the space between the outer peripheral face of the inner peripheral surface of the cylinder body and the rotary piston；
Blade groove, the blade groove is arranged at the cylinder body, and it is free to advance or retreat that the blade, which is housed,
The a plurality of refrigerant flow path is set with running through the cylinder body of the 1st compression mechanism and the cylinder body of the 2nd compression mechanism,
Check-valves is provided with the 1st silencer room side of the 1st discharge port, the check-valves has needle spring plate valve structure
Make, and at one end with fixing end,
1st discharge port staggers in the circumference centered on the bent axle along a direction of rotation with the fixing end matches somebody with somebody
Put,
Being configured on the direction of rotation away from the farthest position of the 1st discharge port in a plurality of refrigerant flow path
Refrigerant flow path, the sectional area with less than other at least 1 refrigerant flow path.
2. multi-cylinder hermetic type compressor according to claim 1, wherein,
, will be described when in the circumference centered on the bent axle, the position of the blade groove of the 1st compression mechanism is set into 0 °
When direction of rotation is set to positive direction,
The a plurality of refrigerant flow path is in the angular range for being circumferentially arranged at 90 °~270 ° centered on the bent axle.
3. multi-cylinder hermetic type compressor according to claim 1 or 2, wherein,
The outlet has the 1st outlet and the 2nd outlet,
, will be described when in the circumference centered on the bent axle, the position of the blade groove of the 1st compression mechanism is set into 0 °
When direction of rotation is set to positive direction,
1st outlet reaches the position of angle, θ 1 in being circumferentially arranged at centered on the bent axle,
2nd outlet reaches the position of angle, θ 2 in being circumferentially arranged at centered on the bent axle,
The a plurality of refrigerant flow path is in the angular range for being circumferentially arranged at 1~θ of θ 2 centered on the bent axle.
4. multi-cylinder hermetic type compressor according to any one of claim 1 to 3, wherein,
The a plurality of respective inflow entrance of refrigerant flow path and flow export are provided with opening portion, the opening portion, which has, to be more than
The sectional area of the respective sectional area of a plurality of refrigerant flow path.
5. a kind of multi-cylinder hermetic type compressor, wherein,
The multi-cylinder hermetic type compressor includes：
Closed container；
Compression unit, the compression unit is housed in the closed container, with the 1st compression mechanism and the 2nd compression mechanism；
Driving force is delivered to the compression unit by bent axle, the bent axle；
1st silencer room of ring-type, the 1st silencer room of the ring-type is configured on the shaft core direction of the bent axle in the pressure
One side in contracting portion, the refrigerant that have compressed in the 1st compression mechanism is discharged to the 1st silencer via the 1st discharge port
Room；
2nd silencer room of ring-type, the 2nd silencer room of the ring-type is configured on the shaft core direction in the compression unit
Another side, the refrigerant that have compressed in the 2nd compression mechanism is discharged to the 2nd silencer room via the 2nd discharge port,
At least 1 refrigerant flow path, at least 1 article refrigerant flow path makes the 1st silencer room and the 2nd silencer room
It is connected, the refrigerant of the 2nd muffler chambers is directed to the 1st silencer room；
The refrigerant of 1st muffler chambers is discharged to the space in the closed container by outlet, the outlet,
1st compression mechanism and the 2nd compression mechanism have respectively：
Cylinder body；
Rotary piston, inner peripheral surface of the rotary piston along the cylinder body carries out eccentric rotary；
Blade, the blade separates the space between the outer peripheral face of the inner peripheral surface of the cylinder body and the rotary piston；
Blade groove, the blade groove is arranged at the cylinder body, and it is free to advance or retreat that the blade, which is housed,
At least 1 article refrigerant flow path is set with running through the cylinder body of the 1st compression mechanism and the cylinder body of the 2nd compression mechanism
Put,
Total sectional area S [the mm of at least 1 refrigerant flow path2] every turn of discharge capacity Vst of 1 time with the 2nd compression mechanism
[cc] meets 8.9 [mm2/cc]<S/Vst<24[mm2/ cc] relation.
6. multi-cylinder hermetic type compressor according to claim 5, wherein,
Check-valves is provided with the 1st silencer room side of the 1st discharge port, the check-valves has needle spring plate valve structure
Make, and at one end with fixing end,
1st discharge port staggers in the circumference centered on the bent axle along a direction of rotation with the fixing end matches somebody with somebody
Put,
, will be described when in the circumference centered on the bent axle, the position of the blade groove of the 1st compression mechanism is set into 0 °
When direction of rotation is set to positive direction,
At least 1 refrigerant flow path is in the angular range for being circumferentially arranged at 90 °~270 ° centered on the bent axle.
7. the multi-cylinder hermetic type compressor according to claim 5 or 6, wherein,
Check-valves is provided with the 1st silencer room side of the 1st discharge port, the check-valves has needle spring plate valve structure
Make, and at one end with fixing end,
1st discharge port staggers in the circumference centered on the bent axle along a direction of rotation with the fixing end matches somebody with somebody
Put,
The outlet includes the 1st outlet and the 2nd outlet,
, will be described when in the circumference centered on the bent axle, the position of the blade groove of the 1st compression mechanism is set into 0 °
When direction of rotation is set to positive direction,
1st outlet reaches the position of angle, θ 1 in being circumferentially arranged at centered on the bent axle,
2nd outlet reaches the position of angle, θ 2 in being circumferentially arranged at centered on the bent axle,
At least 1 refrigerant flow path is in the angular range for being circumferentially arranged at 1~θ of θ 2 centered on the bent axle.
8. the multi-cylinder hermetic type compressor according to any one of claim 5 to 7, wherein,
The inflow entrance and flow export of at least 1 refrigerant flow path are provided with opening portion, the opening portion, which has, to be more than
The sectional area of the sectional area of at least 1 refrigerant flow path.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPPCT/JP2015/050397 | 2015-01-08 | ||
| PCT/JP2015/050397 WO2016110982A1 (en) | 2015-01-08 | 2015-01-08 | Multi-cylinder hermetic compressor |
| PCT/JP2015/076138 WO2016111048A1 (en) | 2015-01-08 | 2015-09-15 | Multi-cylinder hermetic compressor |
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| Publication Number | Publication Date |
|---|---|
| CN107110160A true CN107110160A (en) | 2017-08-29 |
| CN107110160B CN107110160B (en) | 2019-04-23 |
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| CN201580061211.9A Active CN107110160B (en) | 2015-01-08 | 2015-09-15 | Multi-cylinder hermetic type compressor |
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| Country | Link |
|---|---|
| JP (1) | JP6257806B2 (en) |
| CN (1) | CN107110160B (en) |
| WO (2) | WO2016110982A1 (en) |
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| JP7044463B2 (en) * | 2016-11-14 | 2022-03-30 | 株式会社富士通ゼネラル | Rotary compressor |
| CN107339239A (en) * | 2017-07-28 | 2017-11-10 | 广东美芝制冷设备有限公司 | Compressor and humidity control system |
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| JPH01170775A (en) * | 1987-12-25 | 1989-07-05 | Hitachi Ltd | Compressor |
| US5098266A (en) * | 1989-09-08 | 1992-03-24 | Mitsubishi Denki Kabushiki Kaisha | Lubrication of a horizontal rotary compressor |
| JP2000320479A (en) * | 1999-05-12 | 2000-11-21 | Mitsubishi Electric Corp | Multi-cylinder enclosed type compressor |
| CN1326052A (en) * | 2000-05-31 | 2001-12-12 | 三洋电机株式会社 | Electric compressor and refrigerating device therewith |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2005188518A (en) * | 2005-02-24 | 2005-07-14 | Sanyo Electric Co Ltd | Motor driven compressor |
| JP4778772B2 (en) * | 2005-10-26 | 2011-09-21 | 日立アプライアンス株式会社 | Rotary compressor |
| JP4864589B2 (en) * | 2006-08-03 | 2012-02-01 | 三菱電機株式会社 | Multistage rotary compressor |
| JP5237029B2 (en) * | 2008-09-25 | 2013-07-17 | 三菱重工業株式会社 | Rotary compressor |
| JP2011127513A (en) * | 2009-12-18 | 2011-06-30 | Panasonic Corp | Hermetically sealed compressor |
| WO2013140912A1 (en) * | 2012-03-23 | 2013-09-26 | 東芝キヤリア株式会社 | Rotating compressor and freeze-cycle apparatus |
| JP6201341B2 (en) * | 2013-02-28 | 2017-09-27 | 株式会社富士通ゼネラル | Rotary compressor |
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2015
- 2015-01-08 WO PCT/JP2015/050397 patent/WO2016110982A1/en active Application Filing
- 2015-09-15 JP JP2016568276A patent/JP6257806B2/en active Active
- 2015-09-15 WO PCT/JP2015/076138 patent/WO2016111048A1/en active Application Filing
- 2015-09-15 CN CN201580061211.9A patent/CN107110160B/en active Active
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| JPH01170775A (en) * | 1987-12-25 | 1989-07-05 | Hitachi Ltd | Compressor |
| US5098266A (en) * | 1989-09-08 | 1992-03-24 | Mitsubishi Denki Kabushiki Kaisha | Lubrication of a horizontal rotary compressor |
| JP2000320479A (en) * | 1999-05-12 | 2000-11-21 | Mitsubishi Electric Corp | Multi-cylinder enclosed type compressor |
| CN1326052A (en) * | 2000-05-31 | 2001-12-12 | 三洋电机株式会社 | Electric compressor and refrigerating device therewith |
| CN1445460A (en) * | 2002-03-18 | 2003-10-01 | 三洋电机株式会社 | Horizontal rotary compressor |
| CN203717345U (en) * | 2014-02-10 | 2014-07-16 | 广东美芝制冷设备有限公司 | Capacity control type rotary compressor and refrigeration cycle device provided with same |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2016111048A1 (en) | 2016-07-14 |
| CN107110160B (en) | 2019-04-23 |
| JP6257806B2 (en) | 2018-01-10 |
| JPWO2016111048A1 (en) | 2017-06-01 |
| WO2016110982A1 (en) | 2016-07-14 |
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