CN102628442B - Compressor - Google Patents
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- CN102628442B CN102628442B CN201210026048.0A CN201210026048A CN102628442B CN 102628442 B CN102628442 B CN 102628442B CN 201210026048 A CN201210026048 A CN 201210026048A CN 102628442 B CN102628442 B CN 102628442B
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Abstract
Compressor of the present invention, can solve following problem: the high-temperature high-pressure refrigerant gas compressed by compression mechanical part makes motor part be heated because flowing through motor part thus causes the efficiency of motor part to reduce.In the housing (1) that inside becomes discharge atmosphere, be arranged to be separated out the discharge pipe arrangement (21) be provided with the refrigerant gas guide housings outside compressed by compression mechanical part (2) discharge space (40), with the motor space (50) being provided with motor part (3), so the high-temperature high-pressure refrigerant gas compressed by compression mechanical part (2) can not cooled dose of gas-heated by motor part (3), so can realize the high efficiency of motor part.
Description
Technical field
The present invention relates to the compressor for the cooling unit such as cold-warm conditioner and refrigerated warehouse or heat pump type hot watering supply device.
Background technique
In prior art, compressor for aircondition and cooling unit etc. usually comprises compression mechanical part and drives the motor part of this compression mechanical part in housing (casing), plays the refrigerant gas that returns from refrigeration cycle with compression mechanical part compression and is sent into the effect of refrigeration cycle.Usually, the refrigerant gas compressed by compression mechanical part, by temporarily flowing cool motors portion at surrounding motors, is sent to refrigeration cycle (such as with reference to patent documentation 1) from the discharge pipe arrangement being arranged at housing afterwards
Fig. 6 is the longitudinal section of the existing compressor described in patent documentation 1.The refrigerant gas compressed by compression mechanical part 2, is discharged by from exhaust port 18 to the top of compression mechanical part 2.Afterwards, refrigerant gas is by being arranged at the path 52 of the periphery of framework 7, and the top to the motor space 50 between compression mechanical part 2 and motor part 3 is discharged.Part of refrigerant gas, behind cool motors portion 3, discharges by being arranged at the discharge pipe arrangement 21 of discharging space 40.In addition, the refrigerant gas of gas, path 19 between the inwall by being formed at motor part 3 and housing 1, be communicated with the motor space 50 of the upper and lower of motor part 3, after cool motors portion 3, by the rotor of motor part 3 and the gap of stator, entering into the motor space 50 on the top of motor part 3, discharging from being arranged at the discharge pipe arrangement 21 of discharging space 40.
Look-ahead technique document
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 5-44667 publication
Summary of the invention
Invent problem to be solved
But, record in such existing structure at patent documentation 1, the high-temperature high-pressure refrigerant gas after being compressed by compression mechanical part 2, owing to flowing through motor part 3, so motor part 3 cooled doses of gas-heateds, the efficiency of motor part 3 can be caused to reduce.In addition, the Exhaust Gas of high temperature is by being arranged at the path 52 of framework 7 periphery, flow through in the bottom of compression mechanical part 2, so compression mechanical part 2 is heated, the refrigerant gas being in low-temperature condition particularly returned from refrigeration cycle is heated being sent to the process of pressing chamber via suction path.Therefore, have when refrigerant gas is actual be held in inside pressing chamber when, refrigerant gas expand, cause the problem that circulating load reduces.
So the present invention solves above-mentioned existing issue and researches and develops, and object is to provide a kind of compressor, the not cooled dose gas-heated of its motor part, and compression mechanical part can be suppressed in addition to be heated by the refrigerant gas of High Temperature High Pressure.
For solving the method for problem
In the housing that inside is discharge atmosphere, be separated out the discharge space be provided with the discharge pipe arrangement of the refrigerant gas guide housings outside compressed by compression mechanical part, and be provided with the motor space of motor part.
According to this structure, the high-temperature high-pressure refrigerant gas compressed by compression mechanical part is not discharged to outside by motor part from discharge pipe arrangement, so motor part can not cooled dose of gas-heated, thus realizes the high efficiency of motor part.In addition, the suction heating caused because of compression mechanical part cooled dose of gas-heated is suppressed, so can realize the high compressor of volumetric efficiency.
The effect of invention
Compressor of the present invention can realize the high efficiency of motor part.In addition, the high compressor of volumetric efficiency can be realized.
Accompanying drawing explanation
Fig. 1 is the sectional view of the compressor of embodiment of the present invention 1.
Fig. 2 is the cross-sectional view of the compression mechanical part of embodiment of the present invention 1.
Fig. 3 is the figure of the temperature measuring result in each portion in embodiment of the present invention 1.
Fig. 4 is the sectional view of the compressor of embodiment of the present invention 2.
Fig. 5 is the sectional view of the compressor of embodiment of the present invention 3.
Fig. 6 is the longitudinal section of existing compressor.
Description of reference numerals
1 housing
2 compression mechanical parts
3 motor part
18 exhaust ports
20 oil conservators
21 discharge pipe arrangement
40 discharge space
50 motor space
77 bafflers
80 access
81 collision bodies
Embodiment
First invention is a kind of compressor, it is characterized in that: be discharge in the housing of atmosphere in inside, there is the compression mechanical part of compression refrigerant gas and drive the motor part of compression mechanical part, have the discharge pipe arrangement of the refrigerant gas guide housings outside compressed by compression mechanical part at housing, formed in housing: be provided with the discharge space of discharging pipe arrangement and the motor space being provided with motor part, wherein discharge space and motor space are separated.Thus, by the high-temperature high-pressure refrigerant gas that compression mechanical part compresses, be not discharged to contiguously with motor part and discharge space, outside is discharged to afterwards by being arranged at the discharge pipe arrangement of discharging space, so motor part can not cooled dose of gas-heated, the efficiency of motor part can be suppressed to reduce.High efficiency compressor can be realized thus.
Second invention is, by the space of compression mechanical part by the space and the opposing party that are separated into a side in housing, at the spatial placement of a side from the exhaust port of compression mechanical part discharging refrigerant gas, using the space of the opposing party as motor space.Thus, the refrigerant gas of the highest temperature of being discharged from exhaust port by compression mechanical part compression not by motor space, so the refrigerant gas of high temperature can not because of heat transfer heat engines portion, the efficiency of motor part can be suppressed further to reduce.
3rd invention is arrange oil conservator in the bottom of housing, and compression mechanical part is arranged on the position in portion more top than motor part.Thus, because compression mechanical part does not contact with the oil conservator of lower housing portion, so the oil of oil conservator can not be heated by the compression mechanical part being in high temperature because of the heat of compression, oil viscosity can not reduce, and can suppress the slide part reliability deterioration etc. that the efficiency caused because of the sealing reduction of compression mechanical part reduces and causes because oil film is not enough.
4th invention is, using the space of a side as discharge space.Thus, discharge space and motor space are separated by compression mechanical part, so do not passed through motor part by the high-temperature high-pressure refrigerant gas that compression mechanical part compresses, outside is discharged to from the discharge pipe arrangement of discharging spatial placement, so motor part can not cooled dose of gas-heated, the efficiency of motor part can be suppressed further to reduce.More high efficiency compressor can be realized thus.In addition, the high temperature refrigerant gas compressed by compression mechanical part, at compression mechanical part ambient dynamic, can be reduced in the heating that compression mechanical part particularly sucks the refrigerant gas produced in path thus.Thus, suppressed owing to sucking heating, so the high compressor of volumetric efficiency can be realized.
5th invention is, discharges spatial placement in the space of the opposing party.Thus, refrigerant gas is discharged to the space of an above-mentioned side from exhaust port, afterwards by being provided with the discharge space in the space of the opposing party, efficiency can be separated oil in refrigerant gas well thus, the heat exchanger performance in refrigeration cycle can be suppressed to reduce.
6th invention is, arranges the baffler covering exhaust port, is provided with the access of discharging refrigerant gas in housing at baffler.Because the oil playing sealing and lubricity effect is fed into compression mechanical part, although so discharged from exhaust port by the refrigerant gas compressed containing under oil condition, but because baffler covers exhaust port, so can carry out the separation of refrigerant gas contained oil efficiently with this baffler.Afterwards, refrigerant gas, via the access being arranged at baffler, is discharged in housing, afterwards, is discharged to outside, so the heat exchanger performance in refrigeration cycle can be suppressed to reduce from being arranged at the discharge pipe arrangement of discharging space.In addition, the exhaust port in compression mechanical part uses leaf valve that refrigerant gas is discharged, the noise of leaf valve etc. can be reduced with baffler, the compressor of low noise can be realized.
7th invention is that the outlet of the access of baffler is provided with collision body, and this collision body has the plane orthogonal with the flowing of refrigerant gas.Thus, in baffler, the oil contained by refrigerant gas is separated, and carry out collision with the collision body flowing to orthogonal plane of refrigerant gas be separated by being arranged at having of silencing end, more efficiently can carry out the separation of refrigerant gas contained oil thus.
8th invention is, makes the internal face of outlet close to housing of the access of baffler.Thus, due to the internal face of the refrigerant gas containing oil and the housing of discharging from the outlet of the access of baffler can be made to collide, so the separation of refrigerant gas contained oil more efficiently can be carried out.
9th invention is be provided with multiple baffler.Thus, the multiple spaces in baffler are separated the oil contained by refrigerant gas, more efficiently can carry out the separation of refrigerant gas contained oil.In addition, the exhaust port in compression mechanical part uses leaf valve that refrigerant gas is discharged, can the noise of leaf valve etc. be reduced the multiple spaces in baffler, the compressor of more low noise can be realized further.
Tenth invention is, as baffler, arrange the first baffler covering exhaust port and the second baffler covering the first baffler, opening portion and the opening portion of the second baffler of the first baffler clip exhaust port and be configured at relative position.Thereby, it is possible to more efficiently carry out the separation of refrigerant gas contained oil 6 further.
11 invention is, use high-pressure refrigerant such as carbon dioxide as refrigeration agent.When using carbon dioxide coolant, the head pressure of compressor and the pressure difference of suction pressure, up to more than about 7 ~ 10 times of pressure difference of existing refrigeration cycle taking freon as refrigeration agent.Therefore, also easily High Temperature High Pressure is become by the refrigerant gas compressed, but be not discharged to outside by motor part from discharge pipe arrangement by the high-temperature high-pressure refrigerant gas that compression mechanical part compresses, so motor part can not cooled dose of gas-heated, the efficiency of motor part can be suppressed especially to reduce.Therefore, it is possible to realize high efficiency compressor.In addition, the high-temperature high-pressure refrigerant gas compressed by compression mechanical part, at compression mechanical part ambient dynamic, can be reduced in the heating that compression mechanical part particularly sucks the refrigerant gas produced in path thus further.Thus, suppressed owing to sucking heating, so the high compressor of volumetric efficiency can be realized.
Below, with reference to accompanying drawing, embodiment of the present invention is described.In addition, the present invention is not by the restriction of this mode of execution.
(mode of execution 1)
Fig. 1 is the sectional view of the compressor of embodiment of the present invention 1.Below the action of the compressor of present embodiment, effect are described.
As shown in Figure 1, the compressor of present embodiment has the compression mechanical part 2 of compression refrigerant gas and drives the motor part 3 of compression mechanical part 2 in the housing 1 that inside is discharge atmosphere.
Have the discharge pipe arrangement 21 of refrigerant gas guide housings 1 outside compressed by compression mechanical part 2 at housing 1.
Formed in housing 1 and be provided with the discharge space 40 of discharging pipe arrangement 21 and the motor space 50 being provided with motor part 3.
Between main bearing parts 11 and fixed scroll (scroll) 12, clip rotating vortex dish 13, form the compression mechanical part 2 of eddy type.
Discharge space 40 to be separated by compression mechanical part 2 with motor space 50.
That is, the space of the side in the housing 1 be separated by compression mechanical part 2 is formed discharges space 40, and another space in housing 1 forms motor space 50.
Main bearing parts 11 welding or the heat mode such as embedding are fixed in housing 1, and the bearing as crankshaft 4 plays a role.Fixed scroll 12 stop screw rod is fixed on main bearing parts 11.Fixed scroll 12 and rotating vortex dish 13 engage.In addition, between rotating vortex dish 13 and main bearing parts 11, be provided with the rotation limting mechanism 14 that Oudan ring (Oldhamring, partition ring) etc. is formed.Rotation limting mechanism 14 prevents the rotation of rotating vortex dish 13, is guided into by rotating vortex dish 13 and carries out circular orbit motion.Eccentric axial portion 4a is formed in the upper end of crankshaft 4.Eccentric axial portion 4a carries out eccentric drive to rotating vortex dish 13, makes rotating vortex dish 13 carry out circular orbit motion.
Pressing chamber 15 is formed between fixed scroll 12 and rotating vortex dish 13.Pressing chamber 15 is formed between the outer wall of volume (wrap) 12b of fixed scroll 12 and the inwall of the volume 13b of rotating vortex dish 13, between the outer wall being formed at the inwall of the volume 12b of fixed scroll 12 and the volume 13b of rotating vortex dish 13 in addition.Pressing chamber 15 is by while move while diminish carry out compression refrigerant gas from the outer circumferential side of fixed scroll 12 and rotating vortex dish 13 to central part.
Refrigerant gas is inhaled into pressing chamber 15 from the suction path 17 of the suction pipe 16 and fixed scroll 12 peripheral part that lead to housing 1 outside.Then, in pressing chamber 15, reach the refrigerant gas of more than authorized pressure, push leaf valve 19 open from the exhaust port 18 of fixed scroll 12 central part and be discharged.Exhaust port 18 is covered by baffler 77, pushes the refrigerant gas that leaf valve 19 is discharged open, is discharged to silencer space 39.
In addition, motor part 3 is between the main bearing parts 11 and supplementary bearing parts 24 of compression mechanical part 2 bottom.Motor part 3 comprises: by welding or the heat stator 3a being fixed on housing 1 such as embedding, and the rotor 3b be combined into one with crankshaft 4.In addition, for making rotor 3b and the stable rotation of crankshaft 4, making the stable rotation of rotating vortex dish 13, being provided with the counterweight (balanceweight) of pin 22 location at the outer peripheral portion of rotor 3b upper and lower end face.
Rotating vortex dish 13 uses aluminium class material, and fixed scroll 12 uses iron type materials, and main bearing parts 11 use iron type materials.
Slip stripper loop 78 is configured with between the back side and main bearing parts 11 of the wallboard 13a of rotating vortex dish 13.The inside region of slip stripper loop 78 is the high-pressure area 30 of head pressure atmosphere, and the exterior lateral area of slip stripper loop 78 is the back pressure chamber 29 being set to the intermediate pressure be between head pressure and suction pressure.By applying pressure from high-pressure area 30 and back pressure chamber 29, rotating vortex dish 13 stably presses fixed scroll 12, can reduce and leaks and stably carry out circular orbit motion.
The lower end of crankshaft 4 is provided with pump 25.Pump 25 is driven in compressor operation.The oil 6 be located in the oil conservator 20 of setting bottom housing 1 drinks up by pump 25 thus.Oil 6 is supplied to compression mechanical part 2 by the oil supply hole 26 run through in crankshaft 4.Supply pressure now and the head pressure of scroll compressor roughly equal, also become the back pressure source to rotating vortex dish 13.Thus, rotating vortex dish 13 is owing to fixed scroll 12 or can not be separated or monolateral touching, so the stable compression function playing regulation.
A so provided part of oily 6, because of supply pressure and deadweight, enters the embedding part of eccentric axial portion 4a and rotating vortex dish 13 for seeking escape place, and the bearing portion 66 between crankshaft 4 and main bearing parts 11.Then, embedding part and bearing portion 66 lubricated and fall, behind cool motors portion 3, returning oil conservator 20.
On the other hand, be supplied to another part of the oil 6 of the high-pressure area 30 at rotating vortex dish 13 back side, enter into the back pressure chamber 29 residing for rotation limting mechanism 14 by path 51, this path 51 is formed at rotating vortex dish 13 and has an opening end in high-pressure area 30.Enter into the oil 6 of back pressure chamber 29, the slide part of thrust (slide) slide part and rotation limting mechanism 14 is lubricated, and plays the effect applying back pressure with back pressure chamber 29 pairs of rotating vortex dishes 13.And oil 6 is fed into pressing chamber 15, plays the effect of sealing oil.
In addition, compression mechanical part 2, due to portion more top than motor part 3, so be separated with the oil conservator 20 of housing 1 bottom, does not directly contact with oil conservator 20.Therefore, the oil 6 of oil conservator 20 can not be heated by the compression mechanical part 2 becoming high temperature because of the heat of compression thus oil viscosity be reduced, so can suppress the slide part reliability deterioration etc. that the efficiency caused because compression mechanical part 2 sealing reduces reduces and causes because oil film is not enough.
Be described in detail in this compression to refrigerant gas.
Fig. 2 is the cross-sectional view of the compression mechanical part made under rotating vortex dish and fixed scroll engagement.Represent that phase place often staggers the state of 90 degree with the order of Fig. 2 (I) ~ Fig. 2 (IV).At this, the pressing chamber 15 surrounded by the inwall of the outer wall of the volume 13b of rotating vortex dish 13 and the volume 12b of fixed scroll 12 is as the first pressing chamber 15a, and the pressing chamber 15 surrounded by the outer wall of the inwall of the volume 13b of rotating vortex dish 13 and the volume 12b of fixed scroll 12 is as the second pressing chamber 15b.Fig. 2 (I) is the state of the first pressing chamber 15a closed refrigerant gas moment, using this pressing chamber as 15a-1.Afterwards, the first pressing chamber 15a-1 becomes the 15a-2 of (II), the 15a-3 of (III), the 15a-4 of (IV), the 15a-5 of (I), the 15a-6 of (II), the 15a-7 of (III).And the first pressing chamber 15a-8 of (IV) becomes the position of the exhaust port 18 that fixed scroll 12 central part is formed, and the refrigerant gas in the first pressing chamber 15a-8 is discharged from exhaust port 18.
In addition, in embodiments of the present invention, as shown in Figure 1, the refrigerant gas of highest temperature state is in because of high pressure, push leaf valve 19 open with the exhaust port 18 of motor space 50 opposite side be discharged to silencer space 39 from being arranged at, this silencer space 39 is formed by the baffler 77 arranged in the mode covering exhaust port 18.Baffler 77 is provided with access 80, and silencer space 39 is communicated with the discharge space 40 being provided with discharge pipe arrangement 21 by this access 80.Refrigerant gas leaves discharge space 40 and is discharged to the outside from being arranged at the discharge pipe arrangement 21 of discharging space 40.
Fig. 3 is the figure of the temperature measuring result of refrigerant gas under certain operating condition in each portion.As shown in the figure, the temperature measuring result of the refrigerant gas of present embodiment and refrigerant gas are contrasted by the temperature measuring result of the existing structure of motor part 3.At this, use DC brushless motor as motor part 3.Motor part 3 can suppress the heating caused that operates, excellent in efficiency.Refrigerant gas is shown in Fig. 6 by the existing structure of motor part 3.
In contrast, in the present embodiment, as shown in Figure 1, because discharge space 40 and motor space 50 are separated by compression mechanical part 2, so the refrigerant gas of the High Temperature High Pressure compressed by compression mechanical part 2, its part plays the effect that discharge space 40 and motor space 50 are all pressed by the path 52 running through compression mechanical part 2, and mainly enters into discharge space 40 from silencer space 39, is not discharged to housing 1 afterwards outside by motor part 3 from discharge pipe arrangement 21.Thus, because motor part 3 can not cooled dose of gas-heated, so as shown in Figure 3, with refrigerant gas by compared with the existing structure of motor part 3, the temperature of motor part 3 can be made to decline 20 DEG C.
That is, because motor part 3 can not cooled dose of gas-heated, the decrease in efficiency of motor part 3 can be suppressed, so high efficiency compressor can be realized.
In addition, when refrigerant gas does not pass through the present embodiment of motor part 3, compared with existing structure, because the heating of motor space 50 is also suppressed, so the heating of compression mechanical part 2 bottom is also suppressed, the heating of the refrigerant gas of suction path 17 generation that the refrigerant gas under low-temperature condition passes through particularly can be reduced in.And then the heating from housing 1 to the suction path 17 of compression mechanical part 2 is also suppressed.Therefore, suppressed owing to sucking heating, so the high compressor of volumetric efficiency can be realized.
In addition, because the oil 6 playing sealing and lubricity effect is fed into compression mechanical part 2, so discharged from exhaust port 18 by the refrigerant gas compressed containing oil 6, but because baffler 77 is configured to cover exhaust port 18, so can carry out the separation of refrigerant gas contained oil 6 efficiently in silencer space 39.Afterwards, refrigerant gas is via the access 80 being arranged at baffler 77, also the separation of refrigerant gas contained oil 6 can be carried out in discharge space 40, and be discharged to housing 1 outside, so the heat exchanger performance in refrigeration cycle can be suppressed to reduce from being arranged at the discharge pipe arrangement 21 of discharging space 40.
In addition, use leaf valve 19 to make refrigerant gas discharge exhaust port 18, so leaf valve 19 will produce noise, but the noise of leaf valve 19 can be reduced by baffler 77, the compressor of low noise can be realized.At this, be discharged the oil 6 contained by refrigerant gas that space 40 is separated, by running through the gap between the path 52 of compression mechanical part 2 and compression mechanical part 2 and housing 1, fall to motor part 3, returning oil conservator 20.
And arrange collision body 81 in the outlet of the access 80 of baffler 77, this collision body 81 has the plane orthogonal with refrigerant gas flow.
Thus, by being separated the oil 6 in refrigerant gas in baffler 77, and then by be arranged at that baffler 77 exports, have and carry out collision with the collision body 81 of refrigerant gas orthogonal plane and be separated, more efficiently can carry out the separation of refrigerant gas contained oil 6.
In addition, the outlet of the access 80 of baffler 77 is set to make it close to the internal face of housing 1.Thus, due to can make from the outlet of the access 80 of baffler 77 discharge comprise oil the refrigerant gas of 6 and the internal face of housing 1 collide, so the separation of refrigerant gas contained oil 6 more efficiently can be carried out.
(mode of execution 2)
Fig. 4 is the longitudinal section of the compressor of embodiment of the present invention 2.
In the present embodiment, space and another space of a side will be separated in housing 1 by compression mechanical part 2, exhaust port 18 from compression mechanical part 2 discharging refrigerant gas is set in the space 60 of a side, arranges in the space of the opposing party and discharge space 40 and motor space 50.
That is, as shown in the figure, by being provided with the discharge space 40 of discharging pipe arrangement 21, motor part 3 side is arranged at relative to compression mechanical part 2.In addition, discharge space 40 and motor space 50 are separated by demarcation strip 53.
From the refrigerant gas of the High Temperature High Pressure that exhaust port 18 is discharged, first silencer space 39 is expelled to, after the collision of the oil 6 in refrigerant gas being separated by baffler 77 and the internal face of housing 1, relative to compression mechanical part 2, be discharged to the space 60 with motor part 3 opposite side.Afterwards, by running through the path 52 of compression mechanical part 2, be expelled to the discharge space 40 being separated into motor space 50 with demarcation strip 53, in this discharge space 40, the oil 6 in refrigeration agent is separated.At this, demarcation strip 53 discharges space 40 and motor space 50 by making a part for refrigerant gas be communicated with, and also plays the effect that discharge space 40 and motor space 50 are all pressed.
Thereby, it is possible to be efficiently separated the oil 6 in refrigeration agent further, the heat exchanger performance in refrigeration cycle can be suppressed to reduce.
(mode of execution 3)
Fig. 5 is the longitudinal section of the compressor of embodiment of the present invention 3.As shown in the figure, the first baffler 77a and the second baffler 77b is provided with.
The structure such according to Fig. 5, first, oil 6 contained by refrigerant gas is separated in the space in the first baffler 77a, and the refrigerant gas after separation collides in the outlet of the first baffler 77a and the second baffler 77b, and then oil 6 contained by refrigerant gas is separated.Afterwards, collided by collision body 81 and be separated, this collision body 81 is arranged at the outlet of the second baffler 77b, has the plane orthogonal with refrigerant gas.Owing to making the internal face of itself and housing 1 collide further, so the separation of refrigerant gas contained oil 6 more efficiently can be carried out.
First baffler 77a covers exhaust port 18, second baffler 77b and covers the first baffler 77a.And the opening portion 80a of the first baffler 77a and the opening portion 80b of the second baffler 77b, preferably clips exhaust port 18 and is configured in relative position.Thereby, it is possible to more efficiently carry out the separation of refrigerant gas contained oil 6 further.
In addition, the baffler of more than three also can be set.
In addition, in the compressor of mode of execution 3, as shown in Figure 4, by being arranged at motor part 3 side by being provided with the discharge space 40 of discharging pipe arrangement 21 relative to compression mechanical part 2, the separation of refrigerant gas contained oil 6 can more efficiently be carried out further.
In addition, refrigerant gas is made to be discharged to compression mechanical part 2 owing to using leaf valve 19 at exhaust port 18, so can the noise of leaf valve 19 be made to reduce in the multiple spaces in the first baffler 77a, the second baffler 77b, the compressor of more low noise can be realized.
Finally, when working fluid uses high-pressure refrigerant such as carbon dioxide, the head pressure of compressor and the pressure difference of suction pressure large, therefore be also easy to become High Temperature High Pressure by the refrigerant gas compressed, but the mode of execution of the application of the invention, significant especially effect can be presented, the scroll compressor realizing high efficiency, low noise can be provided.
In addition, be illustrated using eddy type as example in the present embodiment, but self-evident, in such as rotary and reciprocating, other compressors, also can obtain equal effect.
Industry utilizes possibility
As mentioned above, compressor of the present invention, can both realize high efficiency, high reliability, and working fluid is not limited to refrigeration agent under various operating condition, also can be applicable to the purposes of the fluid machineries such as air compressor, vacuum pump, decompressor.
Claims (6)
1. a compressor, is characterized in that:
In the housing that inside is discharge atmosphere, there is the compression mechanical part of compression refrigerant gas and drive the motor part of described compression mechanical part,
There is at described housing the discharge pipe arrangement of the described outside that to be led by the refrigerant gas compressed by described compression mechanical part,
Formed in described housing: be provided with the discharge space of described discharge pipe arrangement and be provided with the motor space of described motor part, described discharge space and described motor space are separated by described compression mechanical part, wherein
The bottom of described housing is provided with oil conservator, and described compression mechanical part is arranged on the position in portion more top than described motor part,
Described compressor is provided with discharges described refrigerant gas to the exhaust port in described discharge space and the baffler covering described exhaust port from described compression mechanical part, and described baffler is provided with the access of discharging described refrigerant gas in described housing, and
Described compression mechanical part is provided with the path making described discharge space and described motor space pressure equalization,
A part for described refrigerant gas after being compressed by described compression mechanical part plays the effect that described discharge space and described motor space are all pressed by the path of through described compression mechanical part, mainly enter into described discharge space from described baffler by the described refrigerant gas after described compression mechanical part compresses, be not discharged to described outside by described motor part from described discharge pipe arrangement.
2. compressor as claimed in claim 1, is characterized in that:
The outlet of described access is provided with collision body, and this collision body has the plane orthogonal with the flowing of described refrigerant gas.
3. compressor as claimed in claim 2, is characterized in that:
Make the internal face of described outlet close to described housing of described access.
4. compressor as claimed in claim 2 or claim 3, is characterized in that:
Be provided with multiple described baffler.
5. compressor as claimed in claim 4, is characterized in that:
As described baffler, arrange the first baffler covering described exhaust port and the second baffler covering described first baffler, the opening portion of described first baffler clips described exhaust port with the opening portion of described second baffler and is configured at relative position.
6. compressor as claimed in claim 1, is characterized in that:
Be used as the carbon dioxide of high-pressure refrigerant as refrigeration agent.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-023606 | 2011-02-07 | ||
| JP2011023606 | 2011-02-07 | ||
| JP2011-108014 | 2011-05-13 | ||
| JP2011108014 | 2011-05-13 |
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| Publication Number | Publication Date |
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| CN102628442A CN102628442A (en) | 2012-08-08 |
| CN102628442B true CN102628442B (en) | 2016-04-20 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201210026048.0A Active CN102628442B (en) | 2011-02-07 | 2012-02-07 | Compressor |
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| JP (1) | JP2012255430A (en) |
| CN (1) | CN102628442B (en) |
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| JP2018035800A (en) * | 2016-09-02 | 2018-03-08 | 日立ジョンソンコントロールズ空調株式会社 | Hermetic electric compressor and refrigeration machine |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0778391B2 (en) * | 1985-07-05 | 1995-08-23 | 松下電器産業株式会社 | Scroll gas compressor |
| JP2522459B2 (en) * | 1990-10-04 | 1996-08-07 | ダイキン工業株式会社 | Scroll type fluid machine |
| JPH05133377A (en) * | 1991-11-12 | 1993-05-28 | Sanyo Electric Co Ltd | Closed type compressor |
| JP3264034B2 (en) * | 1993-04-26 | 2002-03-11 | 松下電器産業株式会社 | Scroll compressor |
| JP2874515B2 (en) * | 1993-05-20 | 1999-03-24 | ダイキン工業株式会社 | Scroll type helium gas compressor |
| JPH11210660A (en) * | 1998-01-29 | 1999-08-03 | Mitsubishi Electric Corp | Scroll compressor |
| JP2000018184A (en) * | 1998-06-30 | 2000-01-18 | Toshiba Corp | Rotary compressor |
| JP2006283608A (en) * | 2005-03-31 | 2006-10-19 | Matsushita Electric Ind Co Ltd | Hermetic compressor |
| JP2008008161A (en) * | 2006-06-27 | 2008-01-17 | Sanden Corp | Compressor |
| CN101583777B (en) * | 2007-01-15 | 2012-05-30 | 松下电器产业株式会社 | Expander-integrated compressor |
| JP4799437B2 (en) * | 2007-02-06 | 2011-10-26 | サンデン株式会社 | Fluid machinery |
| JP4962212B2 (en) * | 2007-08-24 | 2012-06-27 | パナソニック株式会社 | Scroll compressor |
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2012
- 2012-01-12 JP JP2012004474A patent/JP2012255430A/en active Pending
- 2012-02-07 CN CN201210026048.0A patent/CN102628442B/en active Active
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| CN102628442A (en) | 2012-08-08 |
| JP2012255430A (en) | 2012-12-27 |
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