CN106032799B - Scroll compressor having a plurality of scroll members - Google Patents
Scroll compressor having a plurality of scroll members Download PDFInfo
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- CN106032799B CN106032799B CN201510110237.XA CN201510110237A CN106032799B CN 106032799 B CN106032799 B CN 106032799B CN 201510110237 A CN201510110237 A CN 201510110237A CN 106032799 B CN106032799 B CN 106032799B
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Abstract
The present invention relates to a scroll compressor, comprising: a housing defining an interior space; a compression mechanism in the housing, including a fixed scroll and a movable scroll, which respectively include an end plate and a wrap in the form of a double scroll, and which are engaged with each other to form a first compression path and a second compression path between the first suction port and the first discharge port, and a third compression path and a fourth compression path between the second suction port and the second discharge port; the scroll compressor further comprises a first air suction pipeline communicated with the first air suction port and a second air suction pipeline communicated with the second air suction port, and a first main electromagnetic valve for controlling the on-off of the air suction pipeline is arranged on the first air suction pipeline. The scroll compressor according to the present invention can precisely adjust the capacity and reduce the pressure fluctuation in the case where the compression mechanism is continuously operated.
Description
Technical field
The present invention relates to a kind of screw compressors, and specifically, the present invention provides one kind can adjust compressor capacity
Double whirlpools formula screw compressor.
Background technique
The content of this part provides only background information relevant to the disclosure, may not constitute the prior art.
Digital scroll compressor utilizes " axial elasticity " technology, and " axial elasticity " allows scroll plate mobile in the axial direction very
Small distance, it is ensured that scroll plate is worked always with optimal power.The control loop period of digital scroll compressor includes one
Section " load phase " and one section " unloading the phase ".During load, compressor works as conventional vortex compressor, transmits and all holds
Amount, compressor output are 100%.During unloading, due to the flexible design of compressor, two scroll plates axially have one it is micro
Separation, there is no refrigerants by compressor, and compressor output is zero.By changing the two times, so that it may adjust compressor
Output capacity.
In the case where compressor is adjusted, i.e., during dynamic vortex part and the engagement of determine vortex part and separation, can generate
Biggish pressure oscillation.Accurate pondage and the double whirlpools formula scroll compression of pressure oscillation can be reduced therefore, it is necessary to a kind of
Machine.
Summary of the invention
One purpose of one or more embodiments of the invention is to provide one kind being capable of accurate pondage and reduction
The double whirlpools formula screw compressor of pressure oscillation.
To achieve the goals above, according to one aspect of the invention, it provides a kind of screw compressors, comprising: shell, shell
Body limits inner space；Compression mechanism in shell, compression mechanism include determine vortex part and dynamic vortex part, determine vortex part
End plate is respectively included with dynamic vortex part and in the whirlpool tooth of double whirlpools form, and determine vortex part and dynamic vortex part intermesh with shape
At the first compressed path and the second compressed path between the first air entry and first row port and it is located at the second air-breathing
Third compressed path and the 4th compressed path between mouth and second exhaust port.Wherein, screw compressor further includes leading to first
First suction line of air entry and the second suction line for leading to the second air entry, are provided with control in the first suction line
First main solenoid valve of the on-off of the suction line.
Thereby, it is possible to adjust the capacity of compressor in the state that compression mechanism continues working, without continually opening
Dynamic and shutdown.When main solenoid valve is closed, corresponding compressed path does not compress refrigerant, to avoid unnecessary function
Consumption.Pulsewidth modulation can be carried out to main solenoid valve and accurate adjust is realized with lower duty ratio.Capacity can directly be adjusted
Pulsewidth modulation and pressure oscillation resulting from are avoided for 50%.
Optionally, lubricant passageway is provided in the end plate of dynamic vortex part, lubricant is supplied to via lubricant passageway
In each compressed path in first to fourth compressed path.
Thereby, it is possible to which lubricant to be supplied in compressed path, to take away the heat that friction generates.
Optionally, in the state that the first main solenoid valve is closed, the first suction line disconnects, near first row port
When temperature exceeds predetermined threshold, the first main solenoid valve opens the predetermined time.
Thereby, it is possible to reduce the temperature of compression mechanism, damage compressor is prevented.
Optionally, it is not provided with main solenoid valve in the second suction line, bypass is formed in the end plate of determine vortex part
Pipeline, bypass line being in third compressed path and screw compressor at the pre-setting line length of the whirlpool tooth of determine vortex part
The position of pressure of inspiration(Pi) is connected to, and is provided with bypass solenoid valve on bypass line to control the on-off of bypass line.
Thereby, it is possible to provide more to determine shelves capacity regulating, and it can be realized and be fine-tuned with lower duty ratio.
Optionally, be formed with bypass line in the end plate of determine vortex part, bypass line determine vortex part whirlpool tooth it is pre-
The first compressed path is connected to the position in pressure of inspiration(Pi) of screw compressor at sizing line length, and in bypass line
On be provided with bypass solenoid valve to control the on-off of bypass line.
Thereby, it is possible to provide more to determine shelves capacity regulating, and it can be realized and be fine-tuned with lower duty ratio.
Optionally, the position in pressure of inspiration(Pi) is the first suction line.
Optionally, the tie point between bypass line and the first suction line is located at the downstream of the first main solenoid valve.
Optionally, bypass solenoid valve is arranged in the open state when the first main solenoid valve is closed, so that part work
Matter recycles in the first compressed path via bypass line.
Thereby, it is possible to which part working medium to be retained in the first compressed path, avoid occurring in the first compressed path serious
Vacuumize phenomenon, to reduce the temperature of compression mechanism.
Optionally, bypass solenoid valve be arranged to when the first main solenoid valve is opened can opening state and closed state it
Between switch, and when in the open position, at least partly working medium in the first compressed path is discharged to the by bypass line
One suction line.
Optionally, the tie point between bypass line and position in pressure of inspiration(Pi) is located at the upper of the first main solenoid valve
Trip.
Optionally, bypass solenoid valve is arranged to be in close state when the first main solenoid valve is closed.
Thereby, it is possible to avoid when main solenoid valve is closed working medium from entering in bypass line around main solenoid valve.
Optionally, bypass solenoid valve be arranged to when the first main solenoid valve is opened can opening state and closed state it
Between switch, and when bypass solenoid valve is opened, at least partly working medium in the first compressed path is discharged to by bypass line
Position in pressure of inspiration(Pi).
Optionally, the whirlpool tooth of the by-pass prot between bypass line and the first compressed path close to determine vortex part is arranged, and
It can be completely covered by the whirlpool tooth of dynamic vortex part, so that by-pass prot intercommunicating pore only leads to the first compressed path.
Thereby, it is possible to avoid by-pass prot from leading to two adjacent compressed paths, and avoid the pressure that may occur therefrom
Release.
Optionally, bypass line leads to first row port, and limited valve is arranged in bypass line, is located at covering
By-pass port between bypass line and the first compressed path, only the pressure at by-pass port is greater than at first row port pressure limiting valve
It is uniaxially opened when pressure at expulsion towards bypass line.
As a result, in the case where by-passing valve is closed, predetermined discharge pressure can be reached in advance in the pressure in compressed path
When, so that the working medium in compressed path is discharged into exhaust outlet via bypass path, to realize the effect for adjusting pressure ratio, and reduces energy
The waste in source.
Optionally, it is provided with only in the downstream of the by-pass port in first row port, between bypass line and first row port
Valve is returned to prevent the gas outside compression mechanism from entering first row port.
Optionally, the first and second compressed paths are connected to by bypass line with the position in pressure of inspiration(Pi), and pressure limiting
Valve has two valve blocks that can be opened and closed independently of each other, and two valve blocks are separately positioned on positioned at bypass line and first
At by-pass port at by-pass port between compressed path and between bypass line and the second compressed path.
Thereby, it is possible to expand the scope of application of bypass line, so as to adjust the output of two compressed paths simultaneously
Capacity.
Optionally, the position in pressure of inspiration(Pi) is the first suction line.
Optionally, the tie point between bypass line and the first suction line is located at the downstream of the first main solenoid valve.
Optionally, bypass solenoid valve is arranged in the open state when the first main solenoid valve is closed, so that the first He
Part working medium in second compressed path recycles in these first compressed paths via bypass line.
Optionally, bypass solenoid valve be arranged to when the first main solenoid valve is opened can opening state and closed state it
Between switch, and when in the open position, pressure limiting valve can be opened based on pressure difference so that in the first and second compressed paths
At least partly working medium be discharged to the first suction line by bypass line.
Optionally, the tie point between bypass line and position in pressure of inspiration(Pi) is located at the upper of the first main solenoid valve
Trip.
Optionally, bypass solenoid valve is arranged to be in close state when the first main solenoid valve is closed.
Optionally, bypass solenoid valve be arranged to when the first main solenoid valve is opened can opening state and closed state it
Between switch, and when in the open position, pressure limiting valve can be opened based on pressure difference so that in the first and second compressed paths
At least partly working medium be discharged to the first suction line by bypass line.
Optionally, the whirlpool tooth of determine vortex part is provided with tooth top seal groove and the sealing element in tooth top seal groove,
Back pressure pipeline is provided in the whirlpool tooth and end plate of determine vortex part with by one in the first suction line and the second suction line
Suction line is connected to tooth top seal groove, and is provided with back pressure solenoid valve in back pressure pipeline to control the logical of back pressure pipeline
It is disconnected.
Thereby, it is possible to adjust the pressure in associated compression path and carrying out pulsewidth modulation to back pressure solenoid valve, thus
Fine-tune capacity.In addition, realizing capacity regulating, energy by the position of adjusting sealing element rather than dynamic, determine vortex part position
Enough further increase efficiency.
Optionally, screw compressor is high side compressors, the first suction line and the first air entry ground company sealed against one another
It connects, the second suction line and the second air entry are connect sealed against one anotherly.
Optionally, screw compressor is low-pressure side compressor, and compression mechanism passes through the first suction line and the second air intake duct
The direct air-breathing in road rather than from the shell of screw compressor air-breathing.
Thereby, it is possible to accurately control the amount into the working medium of suction line.
Optionally, between the first suction line and the first air entry and/or between the second suction line and the second air entry
There are opening portion, opening portion (G) enables the working medium from corresponding suction line partially into the inner space of shell.
Thereby, it is possible to realize the cooling to other components (such as driving mechanism) in enclosure interior space.
Detailed description of the invention
By description referring to the drawings, the feature and advantage of one or several embodiments of the invention will become more
Add and is readily appreciated that.For clarity, it is not necessarily drawn to scale each part in figure, but can be carried out and exaggerate or omit,
In addition, some parts are schematically shown, the physical structure of part is not indicated.In the accompanying drawings:
Fig. 1 shows the generally longitudinally sectional view of the screw compressor of first embodiment according to the present invention；
Fig. 2 and Fig. 3 respectively illustrates the determine vortex part of screw compressor shown in Fig. 1 and the perspective view of dynamic vortex part；
Fig. 4 shows the top cross-sectional view of the compression mechanism of screw compressor shown in Fig. 1；
Fig. 5 shows the longitudinal sectional drawing of the compression mechanism of screw compressor shown in Fig. 1；
Fig. 6 shows the top cross-sectional view of the compression mechanism of the screw compressor of second embodiment according to the present invention；
Fig. 7 shows the longitudinal sectional drawing of the compression mechanism of the screw compressor of second embodiment according to the present invention；
Fig. 8 shows the top cross-sectional view of the compression mechanism of the screw compressor of third embodiment according to the present invention；
Fig. 9 shows the perspective view of the pressure limiting valve in the screw compressor of third embodiment according to the present invention；
Figure 10 shows the longitudinal sectional drawing of the compression mechanism of the screw compressor of third embodiment according to the present invention；
Figure 11 and Figure 12 shows the determine vortex part and dynamic vortex of the screw compressor of the 4th embodiment according to the present invention
The perspective view of part；
Figure 13 shows the longitudinal sectional drawing of the compression mechanism of the screw compressor of second embodiment according to the present invention；
Figure 14 and Figure 15 shows the position A in Figure 13 and is in the enlarged drawing under different conditions；
Figure 16 shows the generally longitudinally sectional view of the screw compressor of the 5th embodiment according to the present invention；
Figure 17 shows the longitudinal sectional drawings of the compression mechanism of screw compressor shown in Figure 16.
Specific embodiment
Description related to the preferred embodiment is only exemplary below, and is definitely not to the present invention and its application or usage
Limitation.The same reference numerals are used to designate identical components in various figures, therefore the construction of same parts will not
Repeat description.
It can be using the essential structure of the screw compressor 1 of one embodiment of the present invention below with reference to Fig. 1 description.
As shown in Figure 1, screw compressor (hereinafter also called compressor) 1 includes substantially closed shell 10.In shell
The compression mechanism CM for being compressed to working medium (such as refrigerant) is accommodated in body 10 and drives the driving of compression mechanism CM
Mechanism DM.In this example, screw compressor 1 designs for high-pressure side.In this field, driving mechanism is usually in pressure at expulsion
The compressor in area (i.e. higher-pressure region) is known as high-pressure side formula compressor, and driving mechanism is in suction pressure region (i.e. low-pressure area)
Compressor is known as low-pressure side formula compressor.Screw compressor 1 is high-pressure side formula compressor, and driving mechanism DM and compression mechanism CM
It is in pressure at expulsion area.It should be appreciated by those skilled in the art that for so-called open compressor design, driving machine
Structure DM also can be set in the outside of shell 10, have no effect on the implementation present invention.
Driving mechanism DM for example may include the motor being made of stator 12 and rotor 14.Stator 12 can use any conjunction
Suitable mode is fixed relative to shell 10.Rotor 14 can rotate within the stator 12 and be provided with drive shaft 16.Driving
Axis 16 is supported by main bearing seat 18 and step 20.One end of drive shaft 16 is formed with eccentric crank pin 16a.Eccentric crank pin
16a cooperation is in the hub 40c of dynamic vortex part 40 to drive compression mechanism CM.Lubricating oil (lubrication is also formed in drive shaft 16
Agent) channel 16b.
Compression mechanism CM may include determine vortex part 30 and dynamic vortex part 40.Determine vortex part 30 can be with any suitable side
Formula is fixed relative to shell 10, such as fixed relative to main bearing seat 18 by bolt, and main bearing seat 18 can be by any
Suitable mode is fixed relative to shell 10.Determine vortex part 30 and dynamic vortex part 40 all have double whirlpools molded line structure, therefore, whirlpool
It revolves compressor 1 and is also known as double whirlpools formula screw compressor.Dynamic vortex part 40 can driven-mechanism DM driving and relative to determining whirlpool
30 translation rotation of rotating part (that is, the central axis of dynamic vortex part 40 is rotated around the central axis of determine vortex part 30, but dynamic vortex part
40 itself will not rotate around the central axis of itself) to realize the compression of fluid.Above-mentioned translation rotation passes through 30 He of determine vortex part
The cross slip-ring being arranged between dynamic vortex part 40 or between dynamic vortex part 40 and main bearing seat 18 realizes (not shown).
As shown in Figures 2 to 5, determine vortex part 30 may include determine vortex part end plate 30a and be formed in determine vortex part end plate
The determine vortex part whirlpool tooth 30b of the side 30a.The first suction is formed at approximately radial opposite position on the periphery of determine vortex part 30
Port In1 and the second air entry In2.First row port is formed in the approximately radial central part of determine vortex part end plate 30a
Out1 and second exhaust port Out2.First row port Out1 is connected with the first air entry In1, second exhaust port Out2 and second
Air entry In2 is connected.It should be appreciated that an exhaust outlet can also only be arranged in determine vortex 30.In first row port Out1 and
Check-valves can be set in second exhaust port Out2 or in shared exhaust outlet, to prevent outside compression mechanism CM
Gas enters exhaust outlet.Dynamic vortex part 40 may include dynamic vortex part end plate 40a, be formed in the side dynamic vortex part end plate 40a
The dynamic vortex part whirlpool tooth 40b and hub 40c for being formed in the other side dynamic vortex part end plate 40a.Determine vortex part whirlpool tooth 30b can with it is dynamic
Scroll whirlpool tooth 40b is intermeshed to be formed together a series of compression with determine vortex part end plate 30a and dynamic vortex part end plate 40a
Path CP.Pressure inside these compressed paths gradually rises from radial outside to radially inner side.Specifically, due to dynamic vortex
Each vortex ring of part whirlpool tooth 40b is separated out two mutual disconnected compressed paths between adjacent determine vortex part whirlpool tooth 30b
CP, so forming the first compressed path CP1 and the second compressed path between the first air entry In1 and first row port Out1
CP2 forms third compressed path CP3 and the 4th compressed path CP4 between the second air entry In2 and second exhaust port Out2.
The improvements of embodiment according to the present invention are described below in detail.As shown in figure 4, in screw compressor 1, it is main
Working medium is introduced into compression mechanism CM by air intake duct 50 from outside compressor 1, and there are two branches for tool at the 50a of end: logical
To the first air entry In1 the first suction line 52 and lead to the second suction line 54 of the second air entry In2.First air intake duct
Road 52 is sealingly engaged with the first air entry In1, and the second suction line 54 is sealingly engaged with the second air entry In2, so that pressure
Hyperbaric environment isolation outside working medium and compression mechanism inside contracting mechanism CM is opened.
It is provided with the first main solenoid valve MV1 in the first suction line 52, it is main that second is provided in the second suction line
Solenoid valve MV2.First main solenoid valve MV1 and the second main solenoid valve MV2 can be turned off or on simultaneously or separately.Work as closing
When, the working medium of respective tube road can not be flowed into corresponding air entry, and corresponding compressed path can not be compressed.By right
Main solenoid valve carry out pulsewidth modulation, can the capacity (i.e. refrigerating capacity) to compressor be adjusted.It is main that first can also be only arranged
One in solenoid valve MV1 and the second main solenoid valve MV2.
When a main solenoid valve (such as the first main solenoid valve MV1) is closed, with the operating of compression mechanism CM, inhaled with first
Working medium in port In1 connected compressed path CP1 and CP2 can be drained out, that is, vacuumize phenomenon.Due to determine vortex
Part 30 and dynamic vortex part 40 high speed moving relative to each other, and lack the cooling of working medium, the temperature of compression mechanism CM in compressed path
Degree will rise rapidly, to influence the structural reliability of compression mechanism CM.In order to prevent this situation, being designed to periodically to
The first of short duration opening of main solenoid valve MV1 such as opens 1s or shorter time, to introduce a small amount of working medium, to prevent compressed path
Middle hypotony and the temperature for preventing compression mechanism CM are more than predetermined threshold.Specifically, can for example by exhaust ports or
Temperature sensor is arranged to detect the delivery temperature near first row port Out1 in first, second compressed path end, and works as
When the delivery temperature detected is more than predetermined threshold, the first main solenoid valve MV1 is made to open the predetermined time.Therefore, it is mentioned below
" substantially close " is not to completely close, but includes this of short duration opening.
In addition, the phenomenon cooling in order to avoid above-mentioned shortage, can also control two main solenoid valves MV1 and MV2, make them
It alternately switchs, to avoid lacking working medium entrance in some air inlet for a long time.Also, due to can not in high side compressors
There can be a degree of leakage phenomenon with avoiding, working medium may be from adjacent compressed path or lubricant passageway as described below
Into in pent compressed path, so that the temperature in pent compressed path will not excessively rise.
It, can be at dynamic vortex part end in order to avoid the temperature in compressed path associated with the main solenoid valve of closing increases
Lubricant passageway 40d is provided in plate 40a, lubricant passageway 40d is near air entry In1 and In2 by corresponding compressed path
CP is connected with dynamic vortex part hub 40c, and then is connected to lubricant passageway 16b.Since the pressure in shell 10 is exhaust pressure
Power, the pressure being higher than in compressed path CP, so a large amount of lubricant is under the action of pressure difference via lubricant passageway 40d
It into compressed path, is left after overcompression by exhaust outlet, to take away the heat that friction generates, prevents compressor damage.
According to the embodiment, during the work time, such as when the first main solenoid valve MV1 is substantially closed, do not freeze
Agent enters the first air entry In1, working medium is compressed using only compressed path relevant to the second air entry In2 at this time, so energy
It is enough that the capacity of compressor is directly adjusted to about the 50% of rated capacity, without frequent starting and shutdown.When main electromagnetism
When valve is closed, corresponding compressed path does not compress refrigerant, to avoid unnecessary power consumption.
Furthermore it is also possible to substantially by a main solenoid valve in the first main solenoid valve MV1 and the second main solenoid valve MV2
When closing, pulsewidth modulation is carried out to another main solenoid valve and realizes adjusting of the capacity from 0% to 50%.For example, in order to realize
25% capacity can substantially close the first main solenoid valve MV1, and the duty ratio for controlling the second main solenoid valve MV2 is 50%,
Such as it is made periodically to close 5s after every opening 5s.It can also be by the first main solenoid valve MV1 and the second main solenoid valve
When a main solenoid valve in MV2 is opened, control the opening/closing the time of another main solenoid valve and realize capacity from 50% to
100% adjusting.Since each main solenoid valve only controls range corresponding with 50% capacity, make it possible to easily realize
More precise control.
It is not sent out by this regulative mode since compressor is in normal operating conditions always during capacity regulating
Raw unloading, because of the problem of pressure oscillation may be not present.Simultaneously when carrying out 50% or less cold regulation, due to can directly close
One air entry, therefore while being adjusted, does not need very high duty ratio.That is, screw compressor according to the present embodiment can
Accurate capacity regulating is realized in the case where compression mechanism runs well, and can be simply implemented and be determined shelves (50%) appearance
Amount.
The second embodiment of screw compressor 1 is described below with reference to Fig. 6, which is in first embodiment
On the basis of the improvement that carries out therefore will omit the description with same section in first embodiment.
In screw compressor 1, it can be provided at least one bypass line 32 in determine vortex part end plate 30a, by this
Siphunculus road 32 is at the pre-setting line length of the whirlpool tooth 30b of determine vortex part 30 by predetermined compressed path CP and the first suction line 52
It is connected to a suction line in the second suction line 54.
Specifically, in the embodiment as shown, the first suction line 52 and the first compressed path CP1 are provided with two
At least one of a bypass line 32a and 32b.Since the second suction line 54 is similar with the first suction line 52, overbottom pressure
Contracting path CP2, CP3 and CP4 is similar with the first compressed path CP1, therefore in the de-scription only in conjunction with the first suction line and first
Compressed path CP1 is described in detail.It is understood that also similar bypass line can be applied to other suction lines and its
Its compressed path.
Wherein, the first bypass line 32a is connected at the first by-pass port 31a with the first compressed path CP1, and is being located at the
It is inhaled from the first tie point 52a in one downstream main solenoid valve MV1 (relative to for the working medium that main air intake duct 50 enters) with first
Air pipe 52 is connected to.Second bypass line 32b is connected at the second by-pass port 31b with the first compressed path CP1, and is being located at the
It is connected at second tie point 52b of one upstream main solenoid valve MV1 with the first suction line 52.In other words, the first bypass line
First compressed path CP1 is connected to by 32a and the second bypass line 32b with the first suction line 52, difference both be only that with
The tie point 52a and 52b of first suction line 52 are located at the downstream and upstream of the first main solenoid valve MV1.
In the present embodiment, in order to make the first bypass line 32a and the second bypass line 32b all lead to the first compression road
Diameter CP1 can without leading to the second compressed path CP2 (it is separated with the first compressed path CP1 by the whirlpool tooth 40b of dynamic vortex part)
Being arranged the first by-pass port 31a and the second by-pass port 31b near the tooth 30b of determine vortex part whirlpool, so that working as dynamic vortex part whirlpool tooth
When 40b is engaged at these by-pass ports with determine vortex part whirlpool tooth 30b, these bypass can be completely covered in dynamic vortex part vortex 40b
Mouthful, each by-pass prot is only connected to a compressed path as a result,.It should be appreciated that arrangement above control merely for convenience, in the phase
In the case where prestige, these by-pass ports can also be disposed across to two compressed paths CP1 and CP2, the first air-breathing will be come from
The two compressed paths of mouth In1 are all connected to the first suction line 52.Even across the compressed path from different air entries,
Such as CP1 and CP3, they are all connected to the upstream of corresponding solenoid valve in the first suction line 52 or the second suction line 54.
On each bypass line 32a and 32b, for example, each bypass line and suction line tie point 52a and
At 52b, the first bypass solenoid valve BV1 and the second bypass solenoid valve BV2 are provided with to independently control corresponding bypass line
On-off.
The case where being put up with when the first main solenoid valve MV1 is opened and closed below describes the course of work of each bypass line.
1. the first main solenoid valve MV1 is opened
When the first main solenoid valve MV1 is opened, for working medium, the first bypass line 32a and the second bypass line 32b
Effect it is similar, therefore by Unify legislation.
1.1 first bypass solenoid valve BV1 or the second bypass solenoid valve BV2 are opened
At this point, working medium enters corresponding first compressed path CP1 from the first air entry In1, and by the first bypass
When mouth 31a, the first suction line 52 is flowed back by the first bypass line 32a by the working medium of partial shrinkage.That is, by first
Pressure reduction at port 31a.In the ideal case, the pressure at the first by-pass port 31a can be reduced to pressure of inspiration(Pi).At this moment, only
The whirlpool flute profile line (also known as remaining whirlpool flute profile line) in the first downstream by-pass port 31a plays the role of compressing working medium, is equivalent to first
The whirlpool flute profile line of bypass line 32a is at pre-setting line length " truncation ".
Assuming that the output capacity that remaining whirlpool flute profile line is realized is full capacity when the second main solenoid valve MV2 is closed
M%.Then when the second main solenoid valve MV2 is also opened, the output capacity that remaining whirlpool flute profile line is realized is the 50%+ of full capacity
0.5 × M%.For example, the output capacity when the second main solenoid valve MV2 is closed is the 34% of full capacity, when the second main electromagnetism
Output capacity when valve MV2 is opened is the 67% of full capacity.Thereby, it is possible to realize in the case where compression mechanism runs well
Accurate capacity regulating, and multi gear capacity (such as 34%, 50%, 67%) can be simply implemented, under certain application environments,
Needs can be met only with shelves capacity is determined, therefore can be avoided and pulsewidth modulation is carried out to solenoid valve, and avoid thus bring
Pressure oscillation.It is of course also possible to be realized by carrying out pulsewidth modulation to main solenoid valve and bypass solenoid valve more accurate stepless
It adjusts, without very high duty ratio.
It similarly,, can be different pre- when the second bypass solenoid valve BV2 is opened for the second bypass line 32b
Whirlpool flute profile line " truncation " will not be repeated again herein with realizing similar accurate adjusting at sizing line length.
In addition, in a suction line in the first suction line 52 and the second suction line 54, such as the second suction line
When being not provided with main solenoid valve on 54, similar bypass line also can be set, which makes such as third compression road
Diameter CP3 is connected to the second suction line 54.The working method of the bypass line will be similar to that above 1.1 described in state, that is,
Bypass solenoid valve can switch between opening state and closed state, and when in the open position, by being partially compressed
Working medium be discharged to corresponding suction line by bypass line.
1.2 first bypass solenoid valve BV1 or the second bypass solenoid valve BV2 are closed
In this case, the first bypass line 32a or the second bypass line 32b do not work, from the first air entry In1
Working medium into the first compressed path CP1 or the second compressed path CP2 is normally compressed.
2. the first main solenoid valve MV1 is closed
At this point, the second bypass solenoid valve BV2 is also accordingly turned off, therefore the second bypass line 32b does not work, to avoid work
Matter enters the first compressed path CP1 via the second bypass solenoid valve BV2 and is compressed.Certainly, in case of need, may be used
To be arranged to make working medium to enter compressed path via the second bypass line 32b, these are arranged without departing from the scope of the present invention.
The course of work of first bypass solenoid valve BV1 will be only discussed below.
2.1 first bypass solenoid valve BV1 are opened
In this case, the pressure during compression working medium of the first compressed path CP1, at the first by-pass port 31a
Power is higher than the pressure at the first tie point 51a, and therefore, working medium, can be due to the first bypass line when by the first by-pass port 31a
The pressure difference of the two sides 32a and return at the first tie point 51a.At least partly working medium is followed in the first compressed path CP1 as a result,
Ring, without being discharged from first row port Out1.Phenomenon is vacuumized in such manner, it is possible to mitigate in the first compressed path CP1, to press down
The temperature raising trend of compression mechanism CM processed, and be conducive to the balance of dynamic vortex part 40.
2.2 first bypass solenoid valve BV1 are closed
In this case, the first bypass line 32a does not work, the compression process in the first compressed path CP1 such as with
Described in upper first embodiment.For example, the first main solenoid valve MV1 intermittently of short duration can be opened to prevent the first compressed path
Temperature in CP1 excessively increases.
Above only describes under the main solenoid valve on and off, each bypass line institute in switching state
Role.It should be appreciated that as required, it is more complicated to realize pulsewidth modulation can be carried out to main solenoid valve and bypass solenoid valve
It is accurate to adjust.
The position of the first by-pass port 31a and the second by-pass port 31b can be properly selected, that is, appropriate selection is provided with side
The pre-setting line length of port (bypass line is connected to by by-pass port with compressed path), so that being remained after by-pass port " truncation "
The length of the remaining whirlpool flute profile line to work has suitable value.Preferably, by-pass port is arranged on the interlude of whirlpool tooth, i.e., away from
Air inlet and exhaust outlet have at the position of certain distance.This is because on the one hand, by-pass port should not be too close to air entry, i.e.,
Remaining whirlpool flute profile line length is unsuitable too long, and otherwise the effect of capacity regulating is unobvious；On the other hand, by-pass port should not be too close to
Exhaust outlet, i.e., remaining whirlpool flute profile line length is unsuitable too short, otherwise when corresponding bypass solenoid valve opens and closes two kinds,
The stress of dynamic vortex part is difficult to balance, for example, pressure in compressed path is too small since molded line length is too short, possibly can not be real
Existing axial elasticity.Preferably, it is provided with molded line exhibition corresponding to the pre-setting line length (measuring since air inlet) of by-pass port
Angle is between 90 ° to 200 °.
The above bypass line shown in figure just for the sake of illustrate each position solenoid valve role and
Function when combination.In practice, it is also not limited to the bypass line that the quantity is set in each compressed path, and bypasses
Pipeline and the tie point of suction line can be in the upstreams or downstream of main solenoid valve.
The third embodiment of screw compressor 1 is described below with reference to Fig. 8 to Figure 10, which is real first
The improvement carried out on the basis of mode is applied, therefore, the description with same section in first embodiment will be omitted.
Third bypass line 32c is provided in the end plate 30a of determine vortex part.Third bypass line 32c is being located at first
It is connected at the third tie point 52c of the upstream main solenoid valve MV1 with the first suction line 52.Also, third bypass line 32c is
It is connected to respectively with the first compressed path CP1 and the second compressed path CP2 at three by-pass port 31c and the 4th by-pass port 31d, that is, the
Three by-pass port 31c and the 4th by-pass port 31d are arranged close to determine vortex part whirlpool tooth 30b, so that as dynamic vortex part whirlpool tooth 40b and determining whirlpool
When the meshing point of rotating part vortex 30b passes through these by-pass ports, these by-pass ports can be completely covered in dynamic vortex part whirlpool tooth 40b.Cause
This, each by-pass port only leads to a compressed path.It is understood that the bypass of third by-pass port 31c and the 4th can also only be arranged
One in mouth 31d, to adjust its corresponding compressed path, it should be understood that in these cases, limit valve described below
Structure will also carry out adaptation.
In third bypass line 32c, such as in the third tie point of third bypass line 32c and the first suction line 52
At 52c, third bypass solenoid valve BV3 is provided with to control the on-off of third bypass line 32c.Below in order to which the simple of description rises
See, third tie point 52c is shown located at the upstream of the first main solenoid valve MV1.
According to above to the description of second embodiment, it will be appreciated by those skilled in the art that as the first main solenoid valve MV1
When closing, third bypass solenoid valve BV3 can also be closed together, to avoid via third bypass line 32c air inlet.And when first
When main solenoid valve MV1 is opened, third bypass solenoid valve BV3 can switch between opening state and closed state.Equally,
In the case that the downstream of the first main solenoid valve MV1 is arranged in three tie point 52c, when the first main solenoid valve MV1 is closed, by third
Three-way electromagnetic valve BV3 opening can be such that part working medium recycles in the first compressed path CP1, and when the first main solenoid valve MV is opened
When, third bypass solenoid valve BV3 can switch between opening state and closed state.It will not be repeated again in these below
Hold, but emphasis is described to the difference of third embodiment and second embodiment.
Third bypass line 32c is further connected in the 5th by-pass port 31e with first row port Out1.Therefore, in third
In the case that bypass solenoid valve BV3 is closed, pressure in third bypass line 32c is the pressure at expulsion of first row port Out1.
On the exhaust outlet Out1 of determine vortex part 30, the downstream of the 5th by-pass port 31e be further provided with check-valves 30f, to avoid outer
The pressure in portion enters in first row port Out1 and third bypass line 32c.
Limited valve RV is set at the by-pass port in third bypass line 32c between compressed path, and pressure limiting valve RV is set
It is set to opening when only the pressure at by-pass port is greater than pressure at expulsion.As an example, as shown in figure 9, pressure limiting valve RV is arc valve
50, the end plate 30a of determine vortex part 30, and flexible first valve block 50a and the second valve block are fixed on by bolt 53
50b, the first valve block 50a and the second valve block 50b are pressed against third by-pass port 31c and the 4th by-pass port 31d respectively, and are arranged to
When the pressure in its corresponding first compressed path CP1 and the second compressed path CP2 is greater than the exhaust in third bypass line 32c
It is uniaxially opened when pressure towards third bypass line 32c.First valve block 50a and the second valve block 50b can independently open or
It closes.
It is opened in corresponding first main solenoid valve MV1 and (or is not provided with the first main solenoid valve MV1, i.e. working medium always can
In from the first suction line 52 into the course of work of the first compressed path CP1 and the second compressed path CP2), when third bypasses
When solenoid valve BV3 is closed, pressure limiting valve RV plays the role of adjusting pressure ratio.Specifically, working as in the first compressed path CP1, third
Pressure in pressure or the second compressed path CP2 at by-pass port 31c, at the 4th by-pass port 31d is greater than first row port
When the pressure of Out1, that is, when overcompression occurs, the first valve block 50a or the second valve block 50b of pressure limiting valve RV is opened, so that accordingly
Compression working medium in compressed path is discharged into first row port Out1 in advance by third bypass line 32c, so as to avoid
Overcompression bring power loss.Pressure at third by-pass port 31c and the 4th by-pass port 31d is respectively less than first row port
When the pressure of Out1, pressure limiting valve RV is closed, and the first compressed path CP1 and the second compressed path CP2 normally compress working medium.
When third bypass solenoid valve BV3 is opened, first row port Out1 and third by-pass port 31c and the 4th by-pass port
The working medium through overcompression or partial shrinkage at 31d drains back into the first suction line 52 by third bypass line 32c, thus makes
By the first compressed path CP1 and the second compressed path CP2 release.Therefore, by carrying out pulsewidth tune to third bypass solenoid valve BV3
System, can compression mechanism CM does not shut down and move, determine vortex part keep engagement in the case where realize capacity regulating.Specifically
Ground, in the case where keeping the first main solenoid valve MV1 to open or be not provided with the first main solenoid valve MV1, as the second main solenoid valve MV2
When closing, it can be adjusted in the range of capacity from 0% to 50% by third bypass solenoid valve BV3；And when second
When main solenoid valve MV2 is opened, it can be carried out in the range of capacity from 50% to 100% by third bypass solenoid valve BV3
It adjusts.
Since third bypass line can be adjusted in 50% section, so can be obtained under lower bypass rate
Lower cooling capacity output is obtained, to reduce due to bypass bring loss, improves the efficiency of cold regulation.In addition, passing through setting
Third by-pass port 31c and the 4th by-pass port 31d can be such that working medium just returns to by these by-pass ports before being fully compressed
Suction line, rather than suction line is returned to by exhaust outlet after complete compression, thus, it is possible to improve efficiency.
Only the first suction line 52 is described in detail above.It is understood that due to the second suction line 54 and first
Suction line 52 is similar, and same third bypass pipe can also be arranged between the second suction line 54 and second exhaust port Out2
Road will not be described in great detail herein.
4th embodiment of screw compressor 1 is described referring to Figure 11 to Figure 15, which is real first
The improvement carried out on the basis of mode is applied, therefore, the description with same section in first embodiment will be omitted.
The whirlpool tooth 30b of the determine vortex part 30 of screw compressor 1 uses tooth top sealing means.Optionally, dynamic vortex part 40
Whirlpool tooth 40b also uses tooth top sealing means.The top of the whirlpool tooth 30b of determine vortex part 30 is provided with tooth top seal groove 34, in tooth
It is provided with sealing element 36 in the seal groove 34 of top, is sealed with the end plate 40a with dynamic vortex part 40.Whirlpool tooth in determine vortex part 30
First compressed path CP1 is spaced apart by a vortex ring of 30b with the 4th compressed path CP4, another vortex ring compresses road for second
Diameter CP2 is spaced apart with third compressed path CP3.The case where two vortex rings, is identical, below will be with the first compressed path CP1 and the 4th
It is described for the sealing element 36 on the tooth 30b of whirlpool between compressed path CP4.End plate 30a and the whirlpool in determine vortex part 30
It is provided with back pressure pipeline 38 in tooth 30b, back pressure pipeline 38 includes the axial component 38a in whirlpool tooth 30b and is located at end plate 30a
In lateral part 38b.The end of the axial component 38a of back pressure pipeline 38 is connected to tooth top seal groove 34, lateral part 38b's
End is connected at the 4th tie point 52d with corresponding suction line (being herein the first suction line 52).In back pressure pipeline 38
In, such as at tie point 52d back pressure solenoid valve BV4 is provided with to control the on-off of back pressure pipeline 38.
The working principle of the back pressure pipeline 38 is described referring to Figure 14 and Figure 15.Figure 14 and Figure 15 show in an exaggerated fashion
The enlarged drawing of tooth top sealing position A is gone out, wherein Figure 14 shows normal operating conditions, and Figure 15 shows the connection of back pressure pipeline 38
State.
As shown in figure 14, in normal work, i.e. when back pressure solenoid valve BV4 is closed, back pressure pipeline 38 disconnects connection, due to
There are pressure difference in the compressed path of 36 two sides of sealing element, sealing element 36 is pressed against tooth top towards the lower side of pressure and is sealed
The side wall of slot 34, and higher pressure can act on the back side of sealing element 36, and sealing element 36 is pressed down against in dynamic whirlpool
The end plate of rotating part realizes tooth top sealing.
As shown in figure 15, when back pressure solenoid valve BV4 is opened, back pressure pipeline 38 is connected to, the pressure at 36 back side of sealing element is
The pressure of inspiration(Pi) introduced by back pressure pipeline 38, lower than the pressure in the compressed path of 36 two sides of sealing element, as a result, sealing element 36
It is pressed against the bottom of tooth top seal groove 34, so that interconnected between the first compressed path CP1 and the 4th compressed path CP4,
And it is connected to air entry and suction pathway to release.However, by dynamic vortex part whirlpool tooth 40b and another determine vortex part whirlpool tooth
Other two compressed path that 30b is separated, i.e. the second compressed path CP2 (being controlled by the first main solenoid valve MV1) and third are compressed
Path CP3 (being controlled by the second main solenoid valve MV2) keeps completely cutting off with the compressed path CP1 and CP4 being relaxed.
In this case, can by back pressure solenoid valve BV4 carry out pulsewidth modulation and control respectively with two air-breathings
The pressure of two compressed paths of mouth connection, to more subtly adjust the capacity of double whirlpools formula screw compressor.In addition, passing through
This capacity regulating mode for adjusting the position of sealing element and realizing is realized with position dynamic, determine vortex part by adjusting
Capacity regulating mode is compared, and efficiency can be further increased.
The screw compressor 100 of 5th embodiment according to the present invention is described below with reference to Figure 16 and Figure 17.With vortex
Compressor 1 is different, and in this example, screw compressor 100 is low-pressure side formula screw compressor, that is, driving mechanism DM, which is located at, to be inhaled
The external environment of atmospheric pressure side, compression mechanism CM is also under pressure of inspiration(Pi).It is above with regard to first other than carrying out following modification
The scheme described to the 4th embodiment can apply to low-pressure side formula screw compressor 100.
Specifically, in screw compressor 100, at least one of the first suction line 52 and the second suction line 54
Opening portion G is provided on path between corresponding air entry, by a small amount of refrigerant leakage to the shell of screw compressor 100
In 110, to cooling driving mechanism DM.Opening portion G can be set at least one suction line, or be arranged in air intake duct
At tie point between road and air entry.It is shown in figure and is located at the second suction line 54 and the second air entry In2 for opening portion G
Between tie point at.Opening portion G is for example positioned at the downstream of corresponding main solenoid valve MV2.
Main bearing seat 18 is not shown in the figure, it will be appreciated by those skilled in the art that in Figure 17 40 two sides of dynamic vortex end plate sky
Between will be closed by main bearing seat 18.
It should be noted that this arrangement and cloth in the prior art of the first suction line 52 and the second suction line 54
Set mode difference.In the prior art, suction line is only connected to shell, and all working medium enter in shell, and compression mechanism CM
Free air-breathing in the housing.In the present embodiment, compression mechanism CM passes through the first suction line 52 and the second suction line 54
Direct air-breathing, only part refrigerant leakage is into shell.In this way, each of compression mechanism CM can be precisely controlled
The inspiratory capacity of air entry.
Screw compressor 100 and screw compressor 1 another difference is that, since the pressure in shell 110 is air-breathing
Pressure, thus described in the second to the 4th embodiment, each bypass line 32a-32d be connected to corresponding air-breathing
One end (that is, one end where 52a-52d) of pipeline may be embodied as free open, without being connect with specific suction line,
It is also able to achieve same release effect in this way.That is, as long as bypass line 32a-32d is connected to i.e. with the position in pressure of inspiration(Pi)
It can.
In addition, the inner space due to screw compressor 100 is in pressure of inspiration(Pi), in order to deliver lubricant to dynamic vortex
In lubricant passageway 40d in part end plate 40b, pumping installations can be set in the lubricant passageway 16b in drive shaft 16
502。
In addition to this, those skilled in the art are reading first to fourth embodiment about high-pressure side formula compressor
Afterwards, low pressure compressor can be applied to, therefore will no longer carry out repeated description.
Although various embodiments of detailed description of the present invention herein, it should be appreciated that the invention is not limited to this
In the specific embodiment being described in detail and show, without departing from the spirit and scope of the present invention can be by this field
Technical staff realizes other modifications and variant.All these modifications and variant are within the scope of the present invention.Moreover, all
Component described herein can be replaced by component equivalent in other technologies.
Claims (27)
1. a kind of screw compressor (1；100), comprising:
Shell (10；110), the shell (10；110) inner space is limited；
Positioned at the shell (10；110) compression mechanism (CM) in, the compression mechanism (CM) include determine vortex part (30) and move
Scroll (40), the determine vortex part (30) and dynamic vortex part (40) respectively include end plate and the whirlpool tooth in double whirlpools form, and
And the determine vortex part (30) and the dynamic vortex part (40) intermesh to be formed and be located at the first air entry (In1) and first row
The first compressed path (CP1) and the second compressed path (CP2) between port (Out1) and it is located at the second air entry (In2)
Third compressed path (CP3) and the 4th compressed path (CP4) between second exhaust port (Out2)；
Wherein, the screw compressor (1；It 100) further include the first suction line (52) for leading to first air entry (In1)
With the second suction line (54) for leading to second air entry (In2), control is provided on first suction line (52)
Make the first main solenoid valve (MV1) of the on-off of first suction line.
2. screw compressor (1 according to claim 1；100), wherein in the end plate (40a) of the dynamic vortex part (40)
In be provided with lubricant passageway (40d), lubricant is supplied to first compressed path via the lubricant passageway (40d)
(CP1), in second compressed path (CP2), the third compressed path (CP3) and the 4th compressed path (CP4)
Each compressed path in.
3. screw compressor (1 according to claim 1；100), wherein first main solenoid valve (MV1) close,
In the state that first suction line (52) disconnects, when the temperature of the first row port (Out1) nearby exceeds predetermined threshold
When, first main solenoid valve (MV1) opens the predetermined time.
4. screw compressor (1 according to claim 1；100), wherein do not set on second suction line (54)
It is equipped with main solenoid valve, is formed with bypass line in the end plate (30a) of the determine vortex part (30), the bypass line is described
By the third compressed path (CP3) and the scroll compression at the pre-setting line length of the whirlpool tooth (30b) of determine vortex part (30)
Machine (1；100) the position connection in pressure of inspiration(Pi), and bypass solenoid valve is provided on the bypass line to control
The on-off of the bypass line.
5. screw compressor (1 according to claim 1；100), wherein in the end plate (30a) of the determine vortex part (30)
In be formed with bypass line (32a；32b；32c), the bypass line (32a；32b；32c) in the whirlpool of the determine vortex part (30)
By first compressed path (CP1) and the screw compressor (1 at the pre-setting line length of tooth (30b)；100) be in is inhaled
The position of atmospheric pressure is connected to, and in the bypass line (32a；32b；Bypass solenoid valve (BV1 is provided on 32c)；BV2；
BV3) to control the bypass line (32a；32b；On-off 32c).
6. screw compressor (1 according to claim 5；100), wherein the position in pressure of inspiration(Pi) is described
First suction line (52).
7. screw compressor (1 according to claim 6；100), wherein the bypass line and first air intake duct
Tie point between road (52) is located at the downstream of first main solenoid valve (MV1).
8. screw compressor (1 according to claim 7；100), wherein the bypass solenoid valve is arranged to when described the
One main solenoid valve (MV1) is in the open state when closing, so that part working medium is via the bypass line in first pressure
Circulation in contracting path (CP1).
9. screw compressor (1 according to claim 7；100), wherein the bypass solenoid valve is arranged to when described the
One main solenoid valve (MV1) can switch when opening between opening state and closed state, and when in the open position, institute
At least partly working medium stated in the first compressed path (CP1) is discharged to first suction line by the bypass line
(52)。
10. screw compressor (1 according to claim 5；100), wherein the bypass line is in pressure of inspiration(Pi) with described
Tie point between the position of power is located at the upstream of first main solenoid valve (MV1).
11. screw compressor (1 according to claim 10；100), wherein the bypass solenoid valve is arranged to when described
First main solenoid valve (MV1) is in close state when closing.
12. screw compressor (1 according to claim 10；100), wherein the bypass solenoid valve is arranged to when described
First main solenoid valve (MV1) can switch when opening between opening state and closed state, and work as the bypass solenoid valve
When opening, at least partly working medium in first compressed path (CP1) is discharged to described in suction by the bypass line
The position of atmospheric pressure.
13. screw compressor (1 according to claim 5；100), wherein the bypass line (32a；32b；32c) with
The whirlpool tooth (30b) of by-pass port close to the determine vortex part (30) between first compressed path (CP1) is arranged, and can
It is completely covered by the whirlpool tooth (40b) of the dynamic vortex part (40), so that the by-pass port only leads to first compressed path
(CP1)。
14. screw compressor (1 according to claim 5；100), wherein the bypass line leads to the first exhaust
Mouthful (Out1), and limited valve (RV) is arranged in the bypass line is located at the bypass line and described the with covering
Third by-pass port (31c) between one compressed path (CP1), the pressure limiting valve (RV) is only at the third by-pass port (31c)
Pressure be greater than the first row port (Out1) at pressure at expulsion when uniaxially opened towards the bypass line.
15. screw compressor (1 according to claim 14；100), wherein in the first row port (Out1), institute
The downstream for stating the 5th by-pass port (31e) between bypass line and the first row port (Out1) is provided with check-valves to prevent
The external gas of the compression mechanism (CM) enters the first row port (Out1).
16. screw compressor (1 according to claim 14；100), wherein the bypass line is compressed described first
Path (CP1) and second compressed path (CP2) are connected to the position in pressure of inspiration(Pi), and the pressure limiting valve
(RV) there are the two valve block (50a that can be opened and closed independently of each other；50b), described two valve block (50a；50b) respectively
It is arranged at the third by-pass port (31c) between the bypass line and first compressed path (CP1) and is located at institute
It states at the 4th by-pass port (31d) between bypass line and second compressed path (CP2).
17. screw compressor (1 according to claim 16；100), wherein the position in pressure of inspiration(Pi) is institute
State the first suction line (52).
18. screw compressor (1 according to claim 17；100), wherein the bypass line and first air-breathing
Tie point between pipeline (52) is located at the downstream of first main solenoid valve (MV1).
19. screw compressor (1 according to claim 18；100), wherein the bypass solenoid valve is arranged to when described
First main solenoid valve (MV1) is in the open state when closing, so that first compressed path (CP1) and second compression
Part working medium in path (CP2) recycles in first compressed path via the bypass line.
20. screw compressor (1 according to claim 18；100), wherein the bypass solenoid valve is arranged to when described
First main solenoid valve (MV1) can switch when opening between opening state and closed state, and when in the open position,
The pressure limiting valve (RV) can be opened based on pressure difference so that first compressed path (CP1) and second compressed path
(CP2) at least partly working medium in is discharged to first suction line (52) by the bypass line.
21. screw compressor (1 according to claim 16；100), wherein the bypass line is in air-breathing with described
Tie point between the position of pressure is located at the upstream of first main solenoid valve (MV1).
22. screw compressor (1 according to claim 21；100), wherein the bypass solenoid valve is arranged to when described
First main solenoid valve (MV1) is in close state when closing.
23. screw compressor (1 according to claim 21；100), wherein the bypass solenoid valve is arranged to when described
First main solenoid valve (MV1) can switch when opening between opening state and closed state, and when in the open position,
The pressure limiting valve (RV) can be opened based on pressure difference so that first compressed path (CP1) and second compressed path
(CP2) at least partly working medium in is discharged to first suction line (52) by the bypass line.
24. screw compressor (1 according to claim 1；100), wherein the whirlpool tooth (30b) of the determine vortex part (30)
The sealing element (36) for being provided with tooth top seal groove (34) and being located in the tooth top seal groove (34), in the determine vortex part
(30) back pressure pipeline (38) is provided in whirlpool tooth (30b) and end plate (30a) with by first suction line (52) and institute
The suction line stated in the second suction line (54) is connected to the tooth top seal groove (34), and in the back pressure pipeline
(38) back pressure solenoid valve (BV4) is provided in control the on-off of the back pressure pipeline (38).
25. according to claim 1 to screw compressor (1 described in any one of 23；100), wherein the screw compressor is
High side compressors, first suction line (52) and first air entry (In1) connect sealed against one anotherly, and described second
Suction line (54) and second air entry (Out1) connect sealed against one anotherly.
26. according to claim 1 to screw compressor (1 described in any one of 23；100), wherein the screw compressor is
Low-pressure side compressor, the compression mechanism (CM) are straight by first suction line (52) and second suction line (54)
Connect air-breathing rather than from the shell of the screw compressor (110) air-breathing.
27. screw compressor (1 according to claim 26；100), wherein first suction line (52) with it is described
There is opening between first air entry (In1) and/or between second suction line (54) and second air entry (In2)
Portion (G), the opening portion (G) enable the working medium from corresponding suction line partially into the shell (110)
Inner space.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510110237.XA CN106032799B (en) | 2015-03-12 | 2015-03-12 | Scroll compressor having a plurality of scroll members |
| PCT/CN2016/072773 WO2016141788A1 (en) | 2015-03-12 | 2016-01-29 | Scroll compressor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510110237.XA CN106032799B (en) | 2015-03-12 | 2015-03-12 | Scroll compressor having a plurality of scroll members |
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| CN106032799A CN106032799A (en) | 2016-10-19 |
| CN106032799B true CN106032799B (en) | 2019-01-25 |
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| CN106762629A (en) * | 2017-01-22 | 2017-05-31 | 西安理工大学 | A kind of fully-closed vortex compressor with double air suction structures |
| CN115013317A (en) * | 2017-03-23 | 2022-09-06 | 艾默生环境优化技术(苏州)有限公司 | Vortex assembly, vortex compressor and compressor heat pump system |
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| CN204511880U (en) * | 2015-03-12 | 2015-07-29 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
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| CN1924360A (en) * | 2005-08-30 | 2007-03-07 | 曹宇 | Multi-line whirl disc of whirl compressor and discharge device thereof |
| CN101205913A (en) * | 2006-12-20 | 2008-06-25 | 乐金电子(天津)电器有限公司 | Power variable device of scroll compressor |
| US7445437B1 (en) * | 2007-06-18 | 2008-11-04 | Scroll Giken Llc | Scroll type fluid machine having a first scroll wrap unit with a scroll member and a scroll receiving member, and a second scroll wrap unit engaged with the first scroll wrap unit |
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