CN208474112U - Screw compressor system and heat-exchange system comprising the screw compressor system - Google Patents
Screw compressor system and heat-exchange system comprising the screw compressor system Download PDFInfo
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- CN208474112U CN208474112U CN201821111618.5U CN201821111618U CN208474112U CN 208474112 U CN208474112 U CN 208474112U CN 201821111618 U CN201821111618 U CN 201821111618U CN 208474112 U CN208474112 U CN 208474112U
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Abstract
The embodiment of the present application provides a kind of screw compressor system and the heat-exchange system comprising the screw compressor system, which includes: variable speed electric motors, particularly；Helical-lobe compressor, with screw rod main shaft, screw rotor bypasses shell and slide valve；And, controller controls the revolving speed of the movement of the slide valve and the shaft of the variable speed electric motors, particularly, wherein, before the revolving speed of the shaft is switched to another rank from a rank, the controller controls the scheduled position that the slide valve is moved to the load reduction for making the helical-lobe compressor.Starting current when the present embodiment can reduce motor switching endangers motor and power grid.
Description
Technical field
This application involves air conditioner technical field more particularly to a kind of screw compressor system and include the screw rod pressure
The heat-exchange system of contracting machine system.
Background technique
Helical-lobe compressor is that most widely used form, helical-lobe compressor are divided into single screw rod and twin-screw in rotary compressor
Two kinds of compressor, single screw rod is made of a screw rod with the spider piece engagement for being distributed in its two sides, and double-screw compressor is by a pair
In parallel, intermeshing yin, yang screw rod is constituted.In single screw compressor or double-screw compressor, the main shaft of screw rod can be with
The rotor of motor connects, and the rotor of motor drives screw turns when rotating, to compress in helical-lobe compressor to refrigerant.
The motor driven to helical-lobe compressor can be constant speed electrode or variable speed electric motors, particularly.Wherein, turn of constant-seed motor
Speed is fixed, and variable speed electric motors, particularly can have the rank (gear) of multiple revolving speeds.
In general, variable speed electric motors, particularly can change revolving speed by the change of the mode of connection, when revolving speed is cut between different ranks
During changing, the corresponding wiring of former revolving speed is disconnected, the corresponding wiring closure of new revolving speed.Therefore, in revolving speed handoff procedure, phase
It is shut down when in motor from former revolving speed, starts to new revolving speed.
It should be noted that the above description of the technical background is intended merely to conveniently carry out clearly the technical solution of the utility model
Chu, complete explanation, and facilitate the understanding of those skilled in the art and illustrate.It cannot be merely because these schemes be practical at this
Novel background technology part is expounded and thinks that above-mentioned technical proposal is known to those skilled in the art.
Utility model content
The inventor of the present application discovered that: during startup, the electric current for flowing through motor can be higher than the specified electricity of motor to motor
Stream, for example, the starting current directly initiated can achieve 6 times of rated current, about with the starting current of star triangular pattern starting
It is 3 times of rated current.
Starting current can cause to impact to motor and power grid, and the time of identical starting current, maintenance is longer, caused by endanger
Evil is bigger, for example, motor is on startup, if the load of helical-lobe compressor is bigger, the time that electric motor starting electric current maintains will
It is longer, it is bigger to the harm of motor itself and power grid, in some instances it may even be possible to motor be caused to burn.
For variable speed electric motors, particularly, speed-changing is equivalent to restarting motor, therefore, if the screw rod in revolving speed switching
The load of compressor is larger, and starting current duration when switching will be longer, to motor itself and power grid bring compared with
Big harm.
The application provides a kind of screw compressor system and the heat-exchange system comprising the screw compressor system, in speed change
Before the revolving speed switching of motor, make the load reduction of helical-lobe compressor, thereby, it is possible to the lower feelings of load in helical-lobe compressor
So that motor is carried out revolving speed switching under condition, starting current duration when motor switches as a result, is shorter, motor and power grid by
To harm be lowered.
According to the embodiment of the present application in a first aspect, providing a kind of screw compressor system, comprising:
Variable speed electric motors, particularly, with rotatable shaft, the shaft can switch between the revolving speed of N number of rank, N be greater than
Or the natural number equal to 2；Helical-lobe compressor, with screw rod main shaft, screw rotor bypasses shell and slide valve, wherein institute
It states screw rod main shaft to connect with the shaft, the screw rotor is set with the screw rod main axis, the periphery of the screw rotor
It is equipped with the bypass shell, slide valve is provided on the bypass shell, the slide valve can be relative to the bypass shell along institute
The axial movement of screw rod main shaft is stated, when the slide valve is mobile to the direction far from shell, forms by-pass port with the bypass shell,
The by-pass port is connected to the compression chamber and suction end of the helical-lobe compressor；And controller, control the movement of the slide valve
With the revolving speed of the shaft of the variable speed electric motors, particularly, wherein be switched to another grade from a rank in the revolving speed of the shaft
Before not, the controller controls the scheduled position that the slide valve is moved to the load reduction for making the helical-lobe compressor.
According to the second aspect of the embodiment of the present application, wherein the scheduled position is that the slide valve makes the by-pass port
Open maximum position.
According to the third aspect of the embodiment of the present application, wherein when the controller needs to make the helical-lobe compressor increment of load
In the case where the first predetermined load, the controller controls the variable speed electric motors, particularly and keeps the rank of current revolving speed, and controls
The slide valve is mobile so that the helical-lobe compressor is to the second predetermined load increment of load.
According to the fourth aspect of the embodiment of the present application, wherein when the helical-lobe compressor increment of load to second predetermined negative
When lotus, the controller: controls the slide valve and be moved to the scheduled position；The variable speed electric motors, particularly is controlled to be switched to than current
The high revolving speed of revolving speed rank；And controlling the slide valve and being moved to keeps the helical-lobe compressor increment of load predetermined to described first
The position of load.
According to the 5th of the embodiment of the present application the aspect, wherein when the controller needs to make the helical-lobe compressor off-load
In the case where third predetermined load, the controller controls the variable speed electric motors, particularly and keeps the rank of current revolving speed, and controls
The slide valve is mobile so that the helical-lobe compressor is to the 4th predetermined load off-load.
According to the 6th of the embodiment of the present application the aspect, wherein when the helical-lobe compressor off-load to the 4th predetermined negative
When lotus, the controller: controls the slide valve and be moved to the scheduled position；The variable speed electric motors, particularly is controlled to be switched to than current
The low revolving speed of revolving speed rank；And the control slide valve is moved to that so that the helical-lobe compressor load is reached the third pre-
The position of constant load.
According to the 7th of the embodiment of the present application aspect, wherein the controller with the helical-lobe compressor according to connecting
The leaving water temperature of evaporator and the comparison result of predetermined temperature set the first predetermined load or third predetermined load.
According to the eighth aspect of the embodiment of the present application, wherein the controller according to the displacement of the slide valve, or according to
The electric current of suction pressure of compressor, Compressor Discharge Pressure and the variable speed electric motors, particularly judges whether the helical-lobe compressor increases
The second predetermined load or off-load are downloaded to the 4th predetermined load.
According to the 9th of the embodiment of the present application the aspect, wherein the gas being discharged from the by-pass port of the helical-lobe compressor
The maximum value of body flow is related with the maximum (top) speed of the variable speed electric motors, particularly and minimum speed.
According to the tenth of the embodiment of the present application the aspect, a kind of heat-exchange system is provided, there is such as above-described embodiment first party
Face screw compressor system described in either side into the 9th aspect, wherein the heat-exchange system for example can be water cooler.
The beneficial effects of the present application are as follows: starting current when can reduce motor switching endangers motor and power grid.
Referring to following description and accompanying drawings, specific implementations of the present application are disclosed in detail, specify the original of the application
Reason can be in a manner of adopted.It should be understood that presently filed embodiment is not so limited in range.In appended power
In the range of the spirit and terms that benefit requires, presently filed embodiment includes many changes, modifications and is equal.
Detailed description of the invention
Included attached drawing is used to provide that a further understanding of the embodiments of the present application, and which constitute one of specification
Point, for illustrating presently filed embodiment, and with verbal description come together to illustrate the principle of the application.Under it should be evident that
Attached drawing in the description of face is only some embodiments of the present application, for those of ordinary skill in the art, is not paying wound
Under the premise of the property made is laborious, it is also possible to obtain other drawings based on these drawings.In the accompanying drawings:
Fig. 1 is a schematic diagram of the screw compressor system of the embodiment of the present application 1；
Fig. 2 is another schematic diagram of the screw compressor system of the embodiment of the present application 1；
Fig. 3 is another schematic diagram of the screw compressor system of the embodiment of the present application 1；
Fig. 4 is another schematic diagram of the screw compressor system of the embodiment of the present application 1；
Fig. 5 is one of process of the screw compressor system in starting and revolving speed switching in the example of the embodiment of the present application 1
A schematic diagram；
Fig. 6 is that compressor load curve in the example of the embodiment of the present application 1, slide valve moving distance curve and variable speed electric motors, particularly turn
One schematic diagram of fast curve；
Fig. 7 is a schematic diagram of the heat-exchange system of the screw compressor system comprising the embodiment of the present application 1；
Fig. 8 is isentropic efficiency-load song of the helical-lobe compressor of the embodiment of the present application 1 and the helical-lobe compressor of the prior art
One schematic diagram of line.
Specific embodiment
Referring to attached drawing, by following specification, the aforementioned and other feature of the application be will be apparent.In specification
In attached drawing, specific implementations of the present application are specifically disclosed, which show wherein can be using the portion of the principle of the application
Divide embodiment, it will thus be appreciated that the application is not limited to described embodiment, on the contrary, the application includes falling into appended power
Whole modifications, modification and equivalent in the range of benefit requirement.
Embodiment 1
The embodiment of the present application provides a kind of screw compressor system, and Fig. 1 is the screw compressor system of the present embodiment
One schematic diagram, Fig. 2 are another schematic diagram of the screw compressor system of the present embodiment, in fig. 1 and 2, the position of slide valve
It moves different.
In the present embodiment, as depicted in figs. 1 and 2, screw compressor system 100 can have: variable speed electric motors, particularly 1, screw rod
Compressor 2 and controller (not shown).
In the present embodiment, variable speed electric motors, particularly 2 can have rotatable shaft 5, which can turn in N number of rank
Switch between speed, wherein N is the quantity of the rank of revolving speed, and N is the natural number more than or equal to 2.For example, revolving speeds at different levels from
It is high to Low to be successively represented as R1, R2..., Rn..., RN, wherein n is natural number and 1≤n≤N.
In the present embodiment, variable speed electric motors, particularly 2 can have a shared stator winding coil, by changing stator winding
Connection type realize the switching of revolving speed, wherein the connection type of stator winding can be switched over by multiple groups switch,
Such as: when second group of switch is disconnected in first group of switch conduction, stator winding can be connected in a manner of a certain, such as with three
The mode of angle scheme connects, and motor can be run at this time with low speed；It is fixed when first group of switch is disconnected in second group of switch conduction
Sub- winding can connect in another way, such as be connected in a manner of Y-Y connection, and motor can be run at high speed at this time.By
This, may be implemented variable speed electric motors, particularly 2 and switch between two kinds of revolving speeds.When motor needs to switch between more middle revolving speeds, can use
Above-mentioned similar mode is realized.
In the present embodiment, helical-lobe compressor 2 can have screw rod main shaft 21, and screw rotor 22 bypasses shell 3, and
Slide valve 32.
As depicted in figs. 1 and 2, screw rod main shaft 21 is connect with shaft 5；Screw rotor 22 is rotated with screw rod main shaft 21；Screw rod
The periphery of rotor 22 is provided with the bypass shell 3；By-pass port 31 (being not shown see Fig. 2, Fig. 1) is offered on bypass shell 3,
In, in Fig. 1, which is completely covered by by slide valve 32, in Fig. 2, since slide valve 32 moves to the left, makes by-pass port 31
Expose；By-pass port 31 is connected to the compression chamber (not shown go out) and suction end (not shown go out) of helical-lobe compressor；Slide valve 32 can position
In by-pass port 31.The slide valve 32 can be relative to by-pass port 31 along the axial movement of the screw rod main shaft 21.
As depicted in figs. 1 and 2, screw rod main shaft 21 is connect with shaft 5；Screw rotor 22 is rotated with screw rod main shaft 21；Screw rod
The periphery of rotor 22 is provided with the bypass shell 3；It is provided with transportable slide valve 32 on bypass shell 3,32 movement of slide valve can
By-pass port 31 (being not shown see Fig. 2, Fig. 1) is formed with shell 3, wherein in Fig. 1, slide valve 32 is not moved, and by-pass port closes 31,
In Fig. 2, slide valve 32 moves to the left, forms by-pass port 31 with bypass shell 3；The compression of the connection helical-lobe compressor of by-pass port 31
Chamber (not shown go out) and suction end (not shown go out).The slide valve 32 is relative to shell 3 along the axial movement of the screw rod main shaft 21, energy
Enough change the size of by-pass port 31.
In the present embodiment, which is capable of the revolving speed of the movement of spool control valve 32 and the shaft 5 of variable speed electric motors, particularly 1,
In, before the revolving speed of shaft 5 is switched to another rank from a rank, which, which controls the slide valve 32 and be moved to, makes the spiral shell
The scheduled position of the load reduction of bar compressor 2.
Pass through shifting before the revolving speed of variable speed electric motors, particularly is switched to another rank from current rank according to the present embodiment
Therefore movable pulley can carry out speed change in the lower situation of load of helical-lobe compressor to reduce the load of helical-lobe compressor
The switching of the speed level of motor, so, speed level switching when starting current duration it is shorter, variable speed electric motors, particularly and
The harm of starting current being subject to for the power grid of variable speed electric motors, particularly power supply is lowered.
In the following, being briefly described in conjunction with working principle of the attached drawing to the helical-lobe compressor of the application.
As shown in Figures 1 and 2, it can be connected by shaft coupling between the shaft 5 and screw rod main shaft 21 of variable speed electric motors, particularly 1.This
Outside, the shaft 5 of variable speed electric motors, particularly 1 can also be same axis with the screw rod main shaft 21 of helical-lobe compressor 2, i.e. turn of variable speed electric motors, particularly 1
Sub (not shown) and screw rotor 22 are sheathed on same axis, also can reach same effect.
When slide valve 32 is mobile to compression chamber, by-pass port 31 is gradually opened, meanwhile, exhaust outlet 321 is to helical-lobe compressor
Compression chamber is close, and air-breathing volume in part is offloaded to suction end from by-pass port 31 in helical-lobe compressor, and the gas being unloaded is not involved in
Refrigeration cycle realizes the load reduction of the off-load compressor of helical-lobe compressor, i.e. off-load to reduce refrigerating capacity；When slide valve 32
When mobile to suction end, by-pass port 31 is progressively closed off, meanwhile, exhaust outlet 321 is close to the suction end of helical-lobe compressor, compressor
Load improve, i.e. increment of load.
Slide valve 32 can be with driving mechanism transmission connection (not shown), which is, for example, motor and feed screw nut
Mechanism Combination or linear motor etc., as long as slide valve 32 can be driven along the axial movement of screw rod main shaft 21, thus open, close or
Adjust 31 openings of sizes of by-pass port.
In the present embodiment, the inner wall for bypassing shell 3 is bonded arrangement with the outer peripheral surface of screw rotor 22.It bypasses on shell 3
Evacuation notch is offered corresponding to the star-wheel 4 being engaged with screw rotor 22.
In Fig. 1 and implementation shown in Fig. 2, helical-lobe compressor 2 is single screw compressor.
In addition, the present embodiment can be without being limited thereto, helical-lobe compressor 2 or double-screw compressor.
Fig. 3 is another schematic diagram of the screw compressor system of the present embodiment, and Fig. 4 is the helical-lobe compressor of the present embodiment
Another schematic diagram of system.In figs. 3 and 4, the displacement of slide valve 32 is different.
As shown in Figures 3 and 4, the screw rotor of double-screw compressor 2 may include male rotor 221 and female rotor 222,
Remaining part is identical as Fig. 1 and Fig. 2, and which is not described herein again.
In the following, being illustrated to the working method of variable speed electric motors, particularly 1 and helical-lobe compressor 2 under control of the controller.
In the present embodiment, when variable speed electric motors, particularly 1 is from lower revolving speed Rn+1It is switched to higher revolving speed RnBefore, the control
Device spool control valve 32 is moved to the scheduled position to make the load reduction of the helical-lobe compressor 2, when to be moved to this pre- for slide valve
When positioning is set, which can control variable speed electric motors, particularly 1 from lower revolving speed Rn+1It is switched to higher revolving speed Rn.In addition, becoming
The revolving speed of speed motor 1 is switched to higher revolving speed Rn+1Afterwards, which can be according to target load come the shifting of spool control valve 32
Dynamic position, so that the load of helical-lobe compressor 2 reaches the target load.
In the present embodiment, when variable speed electric motors, particularly 1 is from higher revolving speed RnIt is switched to lower revolving speed Rn+1Before, the control
Device can control slide valve 32 and be moved to the scheduled position to make the load reduction of helical-lobe compressor 2, when slide valve is moved to this
When predetermined position, which can control variable speed electric motors, particularly 1 from higher revolving speed RnIt is switched to lower revolving speed Rn+1.In addition,
The revolving speed of variable speed electric motors, particularly 1 is switched to lower revolving speed RnAfterwards, which can be according to target load come spool control valve 32
Shift position, so that the load of helical-lobe compressor 2 reaches the target load.
In this embodiment, the controller can according to the detection limit for the displacement sensor being connect with slide valve 23, or according to
The electric current of suction pressure of compressor, Compressor Discharge Pressure and variable speed electric motors, particularly judges whether slide valve is moved to the pre-determined bit
It sets.
In the present embodiment, when variable speed electric motors, particularly 1 starts from closed state, the scheduled position can be located in slide valve 32
In the case where, start variable speed electric motors, particularly 1 from minimum speed, as a result, when variable speed electric motors, particularly starts, the load of helical-lobe compressor compared with
Small, the starting current duration is shorter, and the damage to motor and power grid is smaller.
In addition, above-mentioned side can also be used in the case that the variable speed electric motors, particularly 1 of the present embodiment is replaced by constant-seed motor
Method starts the constant-seed motor, to keep the duration of the starting current of constant-seed motor shorter, to reduce to motor and power grid
Damage.For example, slide valve 32 when starting from closed state, first can be moved to the scheduled position, then by the constant-seed motor
Start constant-seed motor.
In the present embodiment, which can be more makes by-pass port open bigger position relative to current position
It sets, that is, can be the position that slide valve 32 is moved to the left after a distance in Fig. 2, for example, slide valve 32 is moved to the most left of Fig. 2
The position at end, in the position, slide valve 32 can be such that by-pass port 31 is opened to utmostly, that is, in the position, make relative to being located at
For the position that by-pass port 31 is closed, slide valve 32 moves maximum moving distance.
In the following, illustrating process of the screw compressor system of the application in starting and revolving speed switching with an example.
Fig. 5 is a schematic diagram of process of the screw compressor system in starting and revolving speed switching in the example, Fig. 6
It is that one of compressor load curve 601 in the example, slide valve moving distance curve 602 and variable speed electric motors, particularly speed curves 603 shows
It is intended to.
In Fig. 6, horizontal axis indicates the time, and unit is second (S)；Right side longitudinal axis indicates the revolving speed of variable speed electric motors, particularly 1, and unit is
rpm；The longitudinal axis in left side indicates the distance of helical-lobe compressor load and slide valve movement, is expressed as a percentage, that is, helical-lobe compressor
Load be helical-lobe compressor peak load percentage and slide valve 32 moving distance relative to slide valve 32 maximum it is mobile away from
From percentage.
In this example, there are two speed levels for the tool of variable speed electric motors, particularly 1, and revolving speeds at different levels are respectively R1 and R2, wherein R1
It can be 3000 rpms (revolutions per minute, rpm), R2 can be 1500rpm.
In this example, the scheduled position that slide valve is moved to can be the position with maximum moving distance.
As shown in Figure 5 and Figure 6, which may include steps of:
Step 501, slide valve are controlled as being moved to the position with maximum moving distance, and compressor 2 is made to be in minimal negative
Lotus；
Step 502, connect compressor starting current, so that variable speed electric motors, particularly 1 is started to revolving speed R2, wherein step 501 and
Step 502 corresponds to the startup stage of the screw compressor system；
Step 502 can correspond to t1 at the time of Fig. 6 at the time of completion, that is, the revolving speed of variable speed electric motors, particularly 1 is 1500rpm, spiral shell
2 load of bar compressor is 20% load, slide valve 32 in the position with maximum moving distance, wherein 20% load can be
The minimum load of the helical-lobe compressor 2 at revolving speed 1500rpm；
Step 503 keeps the revolving speed R2 of variable speed electric motors, particularly 1 constant, also, reduces the moving distance of slide valve, so that compressor
Increment of load is to scheduled target load, and here, the moving distance of slide valve can for example be reduced to 0%, which can be
Peak load under revolving speed R2, e.g. 50% load, in addition, the scheduled target load is also possible to other lesser values,
The moving distance of slide valve can also be corresponding bigger than 0%；
Step 503 can correspond to t2 at the time of Fig. 6 at the time of completion, the process that the slide valve of step 503 is mobile can be right
Should at the time of Fig. 6 t1 to moment t2 period, in the period, the revolving speed of variable speed electric motors, particularly 1 is 1500rpm, the movement of slide valve away from
0% is changed to from from 100%, so that the load of helical-lobe compressor 2 be made to increase to 50% from 20%, wherein 50% load can be with
It is the peak load of the helical-lobe compressor 2 at revolving speed 1500rpm；
Step 504, slide valve are moved into the position with maximum moving distance, so that the load of compressor becomes the revolving speed
Minimum load under R2, the step 504 can be used as the preparation process before revolving speed is switched to R1 from R2；
Step 504 can correspond to t3 at the time of Fig. 6 at the time of completion, the process that the slide valve of step 504 is mobile can be right
Should at the time of Fig. 6 t2 to moment t3 period, in the period, the revolving speed of variable speed electric motors, particularly 1 is 1500rpm, the movement of slide valve away from
100% is changed to from from 0%, so that the load of helical-lobe compressor 2 be made to be reduced to 20% from 50%；
Step 505, variable-speed motor 1 revolving speed be controlled as being switched to R1；
Step 505 can correspond to t4 at the time of Fig. 6 at the time of completion, and in moment t4, the revolving speed of variable speed electric motors, particularly 1 becomes
3000rpm, the load of helical-lobe compressor 2 are 40%, that is, the minimum load under R1 revolving speed；Wherein, in the period of t3 to t4,
Slide valve 32 is maintained at the position of maximum displacement (i.e. 100%)；
Step 506 keeps the revolving speed R1 of variable speed electric motors, particularly 1 constant, also, reduces the moving distance of slide valve, so that compressor
Increment of load is to scheduled target load, and here, the moving distance of slide valve can for example be reduced to 0%, which can be
Peak load under revolving speed R1, such as can be 100% load；
Step 506 can correspond to t5 at the time of Fig. 6 at the time of completion, the process that the slide valve of step 506 is mobile can be right
Should at the time of Fig. 6 t4 to moment t5 period, in the period, the revolving speed of variable speed electric motors, particularly 1 is 3000rpm, the movement of slide valve away from
From gradually decreasing to 0%, so that the load of helical-lobe compressor 2 be made to be increased to 100% from 40%；
Step 507 increases slide valve moving distance, off-load to 50% load；Here, 50% load is considered speed change
The Rule of judgment of motor speed-changing, that is,, can when making helical-lobe compressor off-load to 50% when by increasing slide valve moving distance
With no longer by increase slide valve moving distance come off-load, but by switch variable speed electric motors, particularly revolving speed to compared with the slow-speed of revolution come off-load；
In addition, in the present embodiment, 50% load is a citing, can also switch the load less than 50% as variable speed electric motors, particularly
The Rule of judgment of revolving speed；
Step 507 can correspond to t6 at the time of Fig. 6 at the time of completion；
Step 508, slide valve are moved into the position with maximum moving distance, so that the load of compressor becomes the revolving speed
Minimum load under R1, the step 508 can be used as the preparation process before revolving speed is switched to R2 from R1；
Step 508 can correspond to t7 at the time of Fig. 6 at the time of completion, the process that the slide valve of step 508 is mobile can be right
Should at the time of Fig. 6 t6 to moment t7 period, in the period, the revolving speed of variable speed electric motors, particularly 1 is 3000rpm, the movement of slide valve away from
From progressively increasing to 100%, so that the load of helical-lobe compressor 2 be made to be reduced to 40% from 50%, wherein 40% load can be
The minimum load of the helical-lobe compressor 2 at revolving speed 3000rpm；
Step 509, variable-speed motor 1 revolving speed be controlled as being switched to R2；Step 509 can correspond at the time of completion
T8 at the time of Fig. 6, in moment t8, the revolving speed of variable speed electric motors, particularly 1 becomes 1500rpm, the load of helical-lobe compressor 2 be 20% when
The period of t7 to t8 is carved, slide valve 2 is maintained at the position of maximum displacement；
Step 510, slide valve are moved, and compressor increment of load is first made, then make compressor off-load to the minimal negative arrived under revolving speed R2
Lotus；
In step 510, slide valve increment of load is to moment t9, and in moment t9, the revolving speed of variable speed electric motors, particularly 1 keeps 1500rpm, sliding
Valve is moved to the position that displacement is 0%, and the load of helical-lobe compressor 2 is 50%；Then, slide valve off-load is to moment t10, slide valve
Reach at maximum displacement, the load of helical-lobe compressor 2 is 20%
Step 511 closes variable speed electric motors, particularly 1.
In the present embodiment, revolving speed of the control device of the screw compressor system 100 in spool control valve and variable speed electric motors, particularly
In the case where with the load of adjustment screw compressor assembly, the movement of slide valve can be adjusted first, it is scheduled negative being unable to reach
In the case where lotus, the speed level of further switch motor can use above-mentioned control when switching the speed level of electrode
Mode.
In one embodiment, the feelings for making the helical-lobe compressor increment of load to the first predetermined load are needed in the controller
Under condition, which controls the rank that current revolving speed can be kept with variable speed electric motors, particularly 1, and spool control valve 32 is mobile so that the screw rod
Compressor is to the second predetermined load increment of load.
If the load of helical-lobe compressor before reaching second predetermined load, does not need to further increase load, then may be used
To switch without the revolving speed of motor.If the load of the helical-lobe compressor reaches the second predetermined load, it is also necessary to continue to mention
High load capacity, the controller improve the control of the revolving speed of motor, it may be assumed that and spool control valve 32 is moved to the scheduled position, then,
Control variable speed electric motors, particularly is switched to the rank of the revolving speed higher than current revolving speed.Second predetermined load, which for example can be, is working as forward
Peak load under speed.In addition, the controller can also control this when variable speed electric motors, particularly is switched to the rank with higher rotation speed
Slide valve 32 is moved to the position for making helical-lobe compressor increment of load to first predetermined load.
In another embodiment, when the controller needs to make 2 off-load of helical-lobe compressor to third predetermined load
In the case of, controller can control variable speed electric motors, particularly 1 and keep the rank of current revolving speed, and it is mobile so that screw rod to control the slide valve 32
Compressor 1 is to the 4th predetermined load off-load.
It, can be without if the load of helical-lobe compressor before reaching the 4th predetermined load, is not necessarily to further off-load
The revolving speed of motor switches.If the load of helical-lobe compressor reaches four predetermined loads, still need to further decrease load, it should
Controller can carry out reducing the control of the revolving speed of motor, it may be assumed that and it controls the slide valve 32 and is moved to the scheduled position, then,
Control variable speed electric motors, particularly 1 is switched to the rank of the revolving speed lower than current revolving speed.That is, the 4th predetermined load can be used as
Judge whether to need to be switched to the Rule of judgment compared with the slow-speed of revolution.Wherein, the 4th predetermined load r, which for example can be, is less than or equal to
Rn/R1 and it is greater than or equal to minimum load of the helical-lobe compressor under current rotating speed, that is, minimum load under current rotating speed≤
R≤Rn/R1, wherein Rn is the rotating speed of target of variable speed electric motors, particularly, that is, the revolving speed after switching, R1 are the maximum speeds of variable speed electric motors, particularly,
For example, when the minimum load under R1 revolving speed is 40%, the 4th predetermined load r is when Rn is 1500rpm, R1 3000rpm
40%≤r≤50%, for example, r=50%, it may be assumed that when motor speed is in R1, if the movement of slide valve 32 arrives compressor off-load
50%, controller, which is judged as, can be switched to revolving speed 1500rpm, and the detailed process of switching is referred to the above-mentioned of the present embodiment
Explanation.
In addition, indicating helical-lobe compressor with percentage in the above description and the following description of the present embodiment
Load, physical meaning are the peak loads of the actual load (unit be kilowatt or standard ton) and helical-lobe compressor of helical-lobe compressor
The percent value of (unit be kilowatt or standard ton).
In addition, the controller can be moved when variable speed electric motors, particularly, which is switched to, has the rank compared with the slow-speed of revolution with spool control valve 32
Moving makes 1 off-load of helical-lobe compressor to the position of the third predetermined load.
In the present embodiment, controller can be according to the leaving water temperature of the evaporator connecting with helical-lobe compressor and predetermined temperature
The comparison result of degree sets first predetermined load or the third predetermined load.
In the present embodiment, which judges the helical-lobe compressor according to the displacement of slide valve 32 whether increment of load is to second
Predetermined load or off-load are to the 4th predetermined load, for example, the displacement of slide valve 32 can be slide valve current location relative to non-moving end position
It moves, the load of the displacement and helical-lobe compressor has corresponding relationship, therefore, the displacement of slide valve 32, it is possible to determine that helical-lobe compressor
Load.Wherein, it can have displacement sensor on slide valve 32, which can detecte the displacement of the slide valve 32.
In addition, the controller can also be according to suction pressure of compressor Ps, Compressor Discharge Pressure Pd and variable speed electric motors, particularly 1
Electric current (for example, electric current that the stator of variable speed electric motors, particularly 1 flows through) to judge the helical-lobe compressor, whether increment of load is second predetermined to this
Load or off-load are to the 4th predetermined load.For example, the ratio of suction pressure of compressor Ps and Compressor Discharge Pressure Pd determine
The electric current of variable speed electric motors, particularly and the relation curve of compressor load, therefore, by calculating the suction pressure of compressor Ps measured
With the ratio of Compressor Discharge Pressure Pd, the electric current of variable speed electric motors, particularly and the relation curve of compressor load can be determined, in conjunction with true
The electric current of the curve and variable speed electric motors, particularly 1 for fixing, available compressor load corresponding with the electric current.
In the following, illustrating the screw compressor system of the application Load adjustment method in heat-exchange system with an example.
Fig. 7 is a schematic diagram of the heat-exchange system of the screw compressor system comprising the present embodiment.
As shown in fig. 7, the heat-exchange system 700 may include: screw compressor system 100, and expansion valve 701, evaporator 702,
And condenser 703.Wherein, which may include variable speed electric motors, particularly 1, helical-lobe compressor 2 and controller
101, wherein for variable speed electric motors, particularly 1, the explanation of helical-lobe compressor 2 and controller 101 is identical as preceding description.In Fig. 7,
The compressed refrigerant of helical-lobe compressor 2 is condensed by condenser, is then throttled by expansion valve, into the refrigerant of evaporator
Heat exchange is carried out with evaporator water is flowed into, the water after heat exchange flows out to form water outlet from evaporator, and the refrigerant after heat exchange enters
Compressor 2 is re-compressed.
As shown in fig. 7, the heat-exchange system 700 for example can be water cooler.Variable speed electric motors, particularly 1 for example can be double speed electricity
The speed of machine, two speed step is respectively: R1 3000rpm, R2 1500rpm.
As shown in fig. 7, controller 101 can detecte the temperature of the water outlet of evaporator 702, movement and electricity by regulating slide valve
The revolving speed of machine adjusts the load of compressor, to control evaporator stable in outlet water temperature in a certain numerical value.
Such as: it is 7 DEG C that group setup, which controls evaporator leaving water temperature,；After compressor start, operating status is low speed
1500rpm, and be minimum load, that is, slide valve is located at maximum displacement；Controller 101 detects 702 leaving water temperature of evaporator, such as
Fruit leaving water temperature is higher than 7 DEG C, needs increment of load compressor load to reduce water temperature, and therefore, controller 101 controls the cunning of compressor 2
Valve displacement reduces so that 2 increment of load of compressor, is 0% when slide valve is reduced to displacement, and compressor load reaches 50% load, at this point,
If water temperature is still higher than 7 DEG C, need to continue to make 2 increment of load of compressor, therefore, 101 switch motor revolving speed of controller to high speed
3000rpm, that is, first spool control valve 32 is moved to displacement maximum, and the revolving speed for then switching electrode is then kept to 3000rpm
The revolving speed, and the displacement of spool control valve is gradually reduced, so that compressor load reaches the level that water temperature is equal to 7 DEG C.
In addition, when compressor operates in high speed 3000rpm, and load is higher, for example, when slide valve is located at least displacement,
If controller 101 detects that 702 leaving water temperature of evaporator lower than 7 DEG C, needs off-load compressor to improve water temperature.Controller
101 are displaced spool control valve increase first so that compressor off-load；When spool displacement increases to maximum, compressor load off-load is arrived
50% load, if water temperature, which still is below 7 DEG C, needs to continue off-load, therefore, 101 switch motor of controller to the slow-speed of revolution
1500rpm, that is, first spool control valve 32 is moved to displacement maximum, and the revolving speed for then switching electrode is then kept to 1500rpm
The revolving speed, and the displacement of spool control valve is gradually reduced, so that compressor load reaches the level that water temperature is equal to 7 DEG C.
In the present embodiment, the maximum value and variable speed electric motors, particularly 1 for the gas flow being discharged from the by-pass port of helical-lobe compressor 31
Maximum (top) speed it is related with minimum speed, wherein the maximum value of gas flow being discharged from the by-pass port 31 of helical-lobe compressor can
To be represented as maximum bypass flow.As a result, compared to the prior art in the screw rod pressure with slide valve that is connect with constant-seed motor
The screw compressor system of contracting machine system, the application reduces bypass gases in sub-load Energy Efficiency Ratio having the same
Amount improves Energy Efficiency Ratio (COP) to reduce invalid acting loss.
In one embodiment, maximum (top) speed and the ratio of minimum speed are bigger, and maximum bypass flow is smaller.For example,
The relationship of maximum bypass flow and maximum (top) speed and minimum speed can be represented as following formula (1):
Maximum bypass flow=100%-A%* (R1/RN)(1)
Wherein, A% is the minimum load of helical-lobe compressor 2, and the screw compression in the case where motor speed is RN
The minimum load of machine 2；R1 is the maximum (top) speed of variable speed electric motors, particularly 1, and RN is the minimum speed of variable speed electric motors, particularly 1.
In the present embodiment, when the load of helical-lobe compressor 2 is 100%, 1 high-speed cruising of variable speed electric motors, particularly, and bypass
Mouth 31 is closed；When the load of helical-lobe compressor is less than 100% and is greater than 50%, 1 high-speed cruising of variable speed electric motors, particularly, and by-pass port
31 open, wherein the load of the adjustable helical-lobe compressor of the opening degree of by-pass port 31 be in 50% to 100% which
Value；When the load of helical-lobe compressor is 50%, the operation of 1 low speed of variable speed electric motors, particularly, and by-pass port 31 is closed；Work as helical-lobe compressor
Load less than 50% when, 1 low speed of variable speed electric motors, particularly operation, and by-pass port 31 open, wherein the opening degree of by-pass port 31
The load of the adjustable helical-lobe compressor is less than which of 50% value.
In the present embodiment, the internal volume when the interior volume specific ratio and load that helical-lobe compressor load is 100% are 50%
Than identical, that is, the displacement of slide valve 32 is identical；When helical-lobe compressor load is less than 100% and is greater than 50%, interior volume specific ratio is less than
The interior volume specific ratio that load is 100%；When the helical-lobe compressor load is less than 50% and is greater than 25%, interior volume specific ratio is less than negative
Interior volume specific ratio when lotus is 50%.
With it is in the prior art include the screw compressor system of constant-seed motor and slide valve compared with, it is negative in helical-lobe compressor
When lotus is lower, the Energy Efficiency Ratio of the helical-lobe compressor of the present embodiment is higher than the prior art.
Fig. 8 is isentropic efficiency-load curve of the helical-lobe compressor of the present embodiment and the helical-lobe compressor of the prior art
One schematic diagram.As shown in figure 8, the longitudinal axis indicates isentropic efficiency, horizontal axis indicates the load of compressor.Wherein, isentropic efficiency can
Reflect the Energy Efficiency Ratio of compressor.Curve 801,802 respectively corresponds the helical-lobe compressor of the present embodiment and the screw rod pressure of the prior art
Isentropic efficiency-load curve of contracting machine, wherein the variable speed electric motors, particularly that the helical-lobe compressor of the present embodiment is connected for example can have
Two speed levels, such as 1500rpm and 3000rpm；The revolving speed for the constant-seed motor that the helical-lobe compressor of the prior art is connected
For example, 3000rpm.From figure 8, it is seen that in the case where load is lower than 60%, the constant entropy of the helical-lobe compressor of the present embodiment
Efficiency is higher than the isentropic efficiency of the helical-lobe compressor of the prior art, that is, the helical-lobe compressor of the present embodiment has higher efficiency
Than.
Pass through shifting before the revolving speed of variable speed electric motors, particularly is switched to another rank from current rank according to the present embodiment
Therefore movable pulley can carry out speed change in the lower situation of load of helical-lobe compressor to reduce the load of helical-lobe compressor
The switching of the speed level of motor, so, speed level switching when starting current duration it is shorter, variable speed electric motors, particularly and
The harm of starting current being subject to for the power grid of variable speed electric motors, particularly power supply is lowered；In addition, in the prior art including constant speed electricity
Machine is compared with the screw compressor system of slide valve, and the Energy Efficiency Ratio of the compressor of the present embodiment is higher.
Embodiment 2
The embodiment of the present application 2 provides a kind of heat-exchange system, which includes helical-lobe compressor system described in embodiment 1
System.It, can be as shown in Figure 7 about the schematic diagram of the heat-exchange system.
The heat-exchange system can have screw compressor system, expansion valve, evaporator and condenser.The heat-exchange system can
To be water cooler or heat pump unit etc..About the explanation of each component of the heat-exchange system, may refer in embodiment 1 for Fig. 7
Explanation.
In the present embodiment, due to the screw compressor system using embodiment 1, can make in screw compressor system
Variable speed electric motors, particularly and be lowered for the harm of starting current that is subject to of power grid of variable speed electric motors, particularly power supply；In addition, the heat-exchange system energy
It is higher to imitate ratio.
The software mould that hardware can be embodied directly in conjunction with the controller that the utility model embodiment describes, executed by processor
Block or both combination.These hardware modules for example these software modules are solidified using field programmable gate array (FPGA) and
It realizes.
Software module can be located at RAM memory, flash memory, ROM memory, eprom memory, EEPROM memory, post
Storage, hard disk, mobile disk, CD-ROM or any other form known in the art storage medium.One kind can be deposited
Storage media is coupled to processor, to enable a processor to from the read information, and can be written to the storage medium
Information；Or the storage medium can be the component part of processor.Pocessor and storage media can be located in ASIC.This is soft
Part module can store in a memory in the mobile terminal, also can store in the storage card that can be inserted into mobile terminal.For example,
If electronic equipment can be deposited using the MEGA-SIM card of larger capacity or the flash memory device of large capacity, the software module
Storage is in the flash memory device of the MEGA-SIM card or large capacity.
For controller described in the present embodiment, the general place for executing function described herein can be implemented as
Reason device, digital signal processor (DSP), specific integrated circuit (ASIC), field programmable gate array (FPGA) other are compiled
Journey logical device, discrete gate or transistor logic, discrete hardware components or it is any appropriately combined.Also it may be implemented
For the combination for calculating equipment, for example, the combination of DSP and microprocessor, multi-microprocessor, communicate with DSP combined one or
Multi-microprocessor or any other this configuration.
Combine specific embodiment that the application is described above, it will be appreciated by those skilled in the art that this
A little descriptions are all exemplary, and are not the limitation to the application protection scope.Those skilled in the art can be according to the application
Spirit and principle various variants and modifications are made to the application, these variants and modifications are also within the scope of application.
Claims (10)
1. a kind of screw compressor system, comprising:
Variable speed electric motors, particularly, with rotatable shaft, the shaft can switch between the revolving speed of N number of rank, and N is to be greater than or wait
In 2 natural number；
Helical-lobe compressor, with screw rod main shaft, screw rotor bypasses shell and slide valve, wherein the screw rod main shaft with
The shaft connection, the screw rotor are provided with the bypass with the screw rod main axis, the periphery of the screw rotor
Shell is provided with slide valve on the bypass shell, and the slide valve can be relative to the bypass shell along the screw rod main shaft
Axial movement forms by-pass port with the bypass shell when slide valve is mobile to the direction far from the bypass shell, described
By-pass port is connected to the compression chamber and suction end of the helical-lobe compressor；And
Controller controls the revolving speed of the movement of the slide valve and the shaft of the variable speed electric motors, particularly,
Wherein, before the revolving speed of the shaft is switched to another rank from a rank, the controller controls the slide valve
It is moved to the scheduled position for the load reduction for making the helical-lobe compressor.
2. screw compressor system as described in claim 1, wherein
The scheduled position is that the slide valve makes the by-pass port open maximum position.
3. screw compressor system as described in claim 1, wherein
In the case that the controller needs to make the helical-lobe compressor increment of load to the first predetermined load,
The controller controls the variable speed electric motors, particularly and keeps the rank of current revolving speed, and controls the slide valve movement so that described
Helical-lobe compressor is to the second predetermined load increment of load.
4. screw compressor system as claimed in claim 3, wherein
When the helical-lobe compressor increment of load is to second predetermined load,
The controller:
It controls the slide valve and is moved to the scheduled position；
Control the rank that the variable speed electric motors, particularly is switched to the revolving speed higher than current revolving speed；And
It controls the slide valve and is moved to the position for making the helical-lobe compressor increment of load to first predetermined load.
5. screw compressor system as described in claim 1, wherein
In the case that the controller needs to make the helical-lobe compressor off-load to third predetermined load,
The controller controls the variable speed electric motors, particularly and keeps the rank of current revolving speed, and controls the slide valve movement so that described
Helical-lobe compressor is to the 4th predetermined load off-load.
6. screw compressor system as claimed in claim 5, wherein
When the helical-lobe compressor off-load is to four predetermined load,
The controller:
It controls the slide valve and is moved to the scheduled position；
Control the rank that the variable speed electric motors, particularly is switched to the revolving speed lower than current revolving speed；And
It controls the slide valve and is moved to the position for making the helical-lobe compressor load reach the third predetermined load.
7. screw compressor system as claimed in claim 3 or 5, wherein
The controller according to the leaving water temperature for the evaporator being connect with the helical-lobe compressor and the comparison result of predetermined temperature,
Set the first predetermined load or third predetermined load.
8. the screw compressor system as described in claim 4 or 6, wherein
The controller is according to the displacement of the slide valve, or according to suction pressure of compressor, Compressor Discharge Pressure and institute
Stating the electric current of variable speed electric motors, particularly, whether increment of load is to the second predetermined load or off-load to the 4th predetermined negative to judge the helical-lobe compressor
Lotus.
9. screw compressor system as described in claim 1, wherein
The maximum value for the gas flow being discharged from the by-pass port of the helical-lobe compressor and the maximum of the variable speed electric motors, particularly turn
Speed is related with minimum speed.
10. a kind of heat-exchange system, comprising: screw compressor system, expansion valve, steaming as claimed in any one of claims 1-9 wherein
Send out device and condenser.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821111618.5U CN208474112U (en) | 2018-07-13 | 2018-07-13 | Screw compressor system and heat-exchange system comprising the screw compressor system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821111618.5U CN208474112U (en) | 2018-07-13 | 2018-07-13 | Screw compressor system and heat-exchange system comprising the screw compressor system |
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| CN208474112U true CN208474112U (en) | 2019-02-05 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108644116A (en) * | 2018-07-13 | 2018-10-12 | 麦克维尔空调制冷(苏州)有限公司 | Screw compressor system and heat-exchange system comprising the screw compressor system |
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2018
- 2018-07-13 CN CN201821111618.5U patent/CN208474112U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108644116A (en) * | 2018-07-13 | 2018-10-12 | 麦克维尔空调制冷(苏州)有限公司 | Screw compressor system and heat-exchange system comprising the screw compressor system |
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