WO2019104811A1

WO2019104811A1 - Screw compressor, air conditioning device, and volume efficiency adjusting method for screw compressor

Info

Publication number: WO2019104811A1
Application number: PCT/CN2017/119262
Authority: WO
Inventors: 刘华; 李日华; 张贺龙; 张天翼; 许云功; 张宝鸽; 侯芙蓉; 刘志华
Original assignee: 格力电器（武汉）有限公司; 珠海格力电器股份有限公司
Priority date: 2017-11-30
Filing date: 2017-12-28
Publication date: 2019-06-06
Also published as: CN107829932B; CN107829932A

Abstract

Disclosed are a screw compressor, an air conditioning device, and a volume efficiency adjusting method for the screw compressor. The screw compressor comprises a body (1), a female rotor (2), a male rotor (3) and an atomization structure, wherein the female rotor (2) and the male rotor (3) are both arranged inside the body (1) and engage with one another; and the atomization structure is arranged inside the body (1), and is used for spraying an atomization oil into a compression cavity (11) formed by the engagement of the female rotor (2) and the male rotor (3). The atomization oil can efficiently seal a triangular leakage region formed between the male rotor (3), the female rotor (2) and the body (1), and enables the leakage amount of a rotor working cavity at a low rotation speed to be less, thus improving the volume efficiency and energy efficiency of the compressor.

Description

Screw compressor, air conditioning equipment and volumetric efficiency adjustment method thereof

The present application is based on the application of the CN application number 201711235474, filed on November 30, 2017, and the priority of which is hereby incorporated by reference.

Technical field

The present disclosure relates to the field of refrigeration technology, and in particular, to a screw compressor, an air conditioning device, and a volumetric efficiency adjustment method thereof.

Background technique

The screw compressor includes a body, a female rotor and a male rotor. The female rotor and the male rotor form a plurality of compression chambers during compression.

The screw compressor is driven by a pair of rotors to compress the gas. When the rotor is engaged, there is a leakage triangle. The gas in the working chamber can be discharged through the leakage triangle. The presence of the leakage triangle reduces the amount of gas actually compressed. The actual air intake will be too small; in the variable frequency screw compressor, the lubricating oil in the working chamber is not easy to form an oil film at low speed, and the sealing can not be achieved. At this time, the gas leaking through the leakage triangle will increase, and the compressor The inspiratory volume is greatly reduced.

The inventors have found that at least the following problems exist in the related art: the leakage triangle has a suction side and a compression side, and since there is no pressure difference between the teeth on the suction side, the influence on the compressor efficiency is negligible; but it is formed during the compression process. The leakage triangle has a problem that the gas leaks due to the large pressure difference between the teeth. When a leak occurs during compression, the actual volumetric flow rate is reduced, resulting in a decrease in the volumetric efficiency of the compressor.

Summary of the invention

The present disclosure proposes a screw compressor, an air conditioning apparatus, and a volumetric efficiency adjustment method thereof for improving the performance of an existing screw compressor and reducing fluid leakage during compression.

The present disclosure provides a screw compressor comprising:

Body

a female rotor disposed inside the body;

a male rotor disposed inside the body and engaging with the female rotor, the female rotor and the male rotor meshing to form a compression chamber;

An atomizing structure is disposed on the body, and the atomizing structure is configured to spray atomized oil into the compression chamber.

In one or more embodiments, the atomization structure includes an oil inlet passage provided in the body, and one end of the injection hole of the oil inlet passage is opposite to the female rotor and/or the male rotor The cogging is connected, and the oil inlet passage is configured to be capable of atomizing the oil.

In one or more embodiments, the atomizing structure further includes a control component that controls conduction and deactivation of the oil inlet passage.

In one or more embodiments, the control component is configured to continuously conduct the oil feed passage when the rotational speed of the screw compressor is lower than a given value; when the rotational speed of the screw compressor When the value is higher than or equal to a given value, the inlet oil passage is periodically turned on.

In one or more embodiments, the oil inlet passage is provided in plurality, and each of the oil inlet passages individually corresponds to one of the female rotor and/or the male rotor.

In one or more embodiments, the oil inlet passage is provided in plurality, and each of the oil inlet passages collectively corresponds to the same slot of the female rotor or the male rotor.

In one or more embodiments, the oil inlet passage is provided in plurality, and the center line of the injection holes of each of the oil inlet passages is located on the first spiral line;

The first spiral is configured to coincide with a helix of the female rotor during rotation of the female rotor; or the first spiral is configured to be used during rotation of the male rotor It coincides with the spiral of the male rotor.

In one or more embodiments, the first spiral is disposed at a position that satisfies a condition that the first spiral is used to coincide with a spiral of the female rotor when the screw compressor begins to vent The first spiral is located between the second slot of the female rotor and the third slot from the exhaust end of the screw compressor to the motor end; or, the first a spiral is used to coincide with the spiral of the male rotor, and when the screw compressor is just starting to exhaust, the first spiral is located from the exhaust end of the screw compressor to the motor end Between the second slot of the male rotor and the third slot.

In one or more embodiments, the oil inlet passage is provided with a plurality of strips, and a center line of the injection holes of each of the oil inlet passages is located on a curve, and the curve includes a first spiral segment and a first a second spiral segment, the curve being configured such that during operation of the compressor, the first spiral segment is for coincidence with a helix of the female rotor, and the second spiral segment is for use with the male rotor The spirals coincide.

In one or more embodiments, the set position of the first spiral segment satisfies the condition that the first spiral segment is used to coincide with the helix of the female rotor, when the screw compressor is just beginning to exhaust The first spiral segment is located between the second slot of the female rotor and the third slot from the exhaust end of the screw compressor to the motor end.

In one or more embodiments, the second spiral segment is disposed at a position that satisfies a condition that the second spiral segment is coincident with a helix of the male rotor when the screw compressor begins to vent The second spiral segment is located between the second slot of the male rotor and the third slot from the exhaust end of the screw compressor to the motor end.

In one or more embodiments, the body is further provided with a return oil passage that communicates with the female rotor and/or the tooth groove of the male rotor.

In one or more embodiments, the return oil passage is provided in plurality, and each of the return oil passages individually corresponds to the female rotor and/or the tooth groove of the male rotor.

In one or more embodiments, the orifice of the oil inlet passage has an inner diameter of from 1 mm to 3 mm.

In one or more embodiments, the other end of the oil inlet path away from the orifice is in communication with the oil groove of the screw compressor.

In one or more embodiments, the control component includes a valve disposed in the oil inlet passage.

An embodiment of the present disclosure further provides an air conditioning apparatus, including the screw compressor provided by any one of the technical solutions of the present disclosure.

The embodiment of the present disclosure further provides a method for adjusting the volumetric efficiency of a screw compressor, comprising the following steps:

An atomized oil is sprayed into the compression chamber formed by the engagement of the female rotor and the male rotor of the screw compressor.

In one or more embodiments, when the rotational speed of the screw compressor is lower than a given value, the atomizing oil is continuously injected into the compression chamber formed by the engagement of the female rotor and the male rotor; When the rotational speed of the screw compressor is higher than or equal to a given value, the atomized oil is periodically injected into the compression chamber formed by the engagement of the female rotor and the male rotor.

The above technical solution is provided with an atomization structure, and the atomization structure can spray oil into the compression chamber, and the atomized oil can effectively seal the triangular leakage area formed between the anode rotor, the cathode rotor and the body body, so that the rotor working chamber leaks at a low rotation speed. The amount is small, the compressor volumetric efficiency is improved, and the compressor energy efficiency is improved; further, by controlling the operation of the atomization structure, the fuel injection amount at high rotation speed can be reduced, and the compressor volumetric efficiency can be further improved.

DRAWINGS

1 is a schematic structural view of a screw compressor according to some embodiments of the present disclosure;

2 is a partial structural schematic view of a screw compressor provided by other embodiments of the present disclosure.

Detailed ways

The technical solution provided by the present disclosure will be described in more detail below with reference to FIGS. 1 to 2 .

Referring to FIG. 1, an embodiment of the present disclosure provides a screw compressor including a body 1, a female rotor 2, a male rotor 3, and an atomizing structure. Both the female rotor 2 and the male rotor 3 are disposed inside the body 1 and are engaged with each other. The atomizing structure is disposed on the body 1, and the atomizing structure is used to inject the atomized oil into the compression chamber 11 formed by the meshing of the female rotor 2 and the male rotor 3.

Further, the atomization structure includes an oil inlet passage 4 provided in the body 1, and one end of the injection hole 41 of the oil inlet passage 4 communicates with the tooth groove of the female rotor 2 and/or the male rotor 3, and the oil inlet passage 4 It is constructed to be able to atomize oil. Specifically, the inlet oil passage 4 may communicate only with the slots of the male rotor 2 or only with the slots of the female rotor 3. Of course, it is also possible to provide communication with the tooth grooves of the male rotor 2 and the female rotor 3 at the same time, and it is possible to achieve simultaneous communication with the tooth grooves of the male rotor 2 and the female rotor 3 by providing a plurality of injection holes 41.

In order to allow the oil sprayed into the compression chamber to be atomized, the inner diameter of the injection hole 41 of the oil inlet passage 4 is 1 mm to 3 mm. For example, it is 1mm, 2mm, 3mm.

In order to facilitate the on/off of the intake oil passage 4, the atomization structure further includes a control member 5 that controls the conduction and the cutoff of the intake oil passage 4. The control member 5 can employ a valve structure such as a solenoid valve.

Alternatively, the control unit 5 is configured to continuously conduct the oil inlet passage 4 when the rotational speed of the male rotor 3 is lower than a given value. When the rotational speed of the male rotor 3 is higher than or equal to a given value, the oil inlet passage 4 is periodically turned on. The set value can be set in advance, and the control unit 5 can include a controller or the like to realize automatic control of the on/off of the oil inlet passage 4.

In the above technical solution, when the screw compressor has a low rotation speed, an oil film seal can be formed at the rotor leakage triangle, the leakage volume of the rotor working chamber is small, the volumetric efficiency is high, and the compressor has high energy efficiency. Moreover, the fuel injection amount can be controlled, and when the screw compressor has a high rotation speed, it can be set to have less fuel injection or no fuel injection, and the volume occupied by the working chamber lubricating oil is small, so that the volumetric efficiency of the compressor is high.

Referring to Fig. 1, a plurality of oil inlet passages 4 are provided, and each of the oil inlet passages 4 individually corresponds to the slots of the female rotor 2 and/or the male rotor 3. In the present embodiment, each of the tooth grooves of the male rotor 2 is separately provided with an oil inlet oil passage 4. Since the triangular leakage area exists in each compression chamber, the oil inlet passage 4 is provided at each of the slots, so that each of the male rotor 3 and the female rotor 2 can be formed in each compression chamber formed during the working process. The atomized oil is sprayed to effectively seal the triangular leakage area, reduce the leakage and improve the performance of the screw compressor.

Further, the body 1 is further provided with a return oil passage that communicates with the slots of the female rotor 2 and/or the male rotor 3. The return oil passage can extract more oil between the slots to reduce the influence of excess oil on the compression volume.

Optionally, a plurality of return oil passages are provided, and each of the return oil passages individually corresponds to the slots of the female rotor 2 and/or the male rotor 3. A control structure for controlling the on/off of each of the return oil passages can be provided.

In order to make rational use of the existing oil of the unit, the other end of the inlet oil passage 4 communicates with the oil groove 6 of the screw compressor.

In the present embodiment, the control unit 5 includes a valve, and the valve is disposed in the oil inlet passage 4. The valve may specifically be a solenoid valve or the like.

A specific embodiment will be described below with reference to the accompanying drawings.

Referring to FIG. 1, a corresponding number of oil inlet passages 4 are disposed on the body 1 corresponding to the rotor cogging position, and each of the oil inlet oil passages 4 has an injection hole 41, and the inner diameter of the injection hole 41 is Φ1 to Φ3, which can After the oil is atomized, it enters the working chamber, and the atomized oil is more likely to form a sealing oil film, and the injection hole 41 is connected to the compressor oil groove 6. A solenoid valve may be disposed between the injection hole 41 and the oil groove 6, and the amount of fuel injection may be controlled by a solenoid valve. When the compressor runs at low speed, the leakage of gas through the leakage triangle increases. At this time, the solenoid valve can be opened, and the oil passage connects the compressor oil groove 6 to the working chamber, and the injection hole 41 of Φ2 can atomize the lubricating oil. The atomized lubricating oil forms a good effect on the oil film. The atomized lubricating oil is mixed with the refrigerant in the working chamber and forms a sealing oil film. The sealing oil film exists at the leakage triangle, which can reduce the gas leakage amount at the leakage triangle and improve the compression. The actual inspiratory volume of the machine, thereby increasing the volumetric efficiency of the compressor. When the compressor is running at high speed, at this time, because the rotation speed is high, the working chamber is easy to form an oil film, and does not need too much lubricating oil. More lubricating oil enters the working chamber and will occupy a part of the volume. At this time, the solenoid valve can be passed. If the pulse is 1 stop 10, for example, 1 second is stopped for 10 seconds to reduce the fuel injection amount, reduce the volume occupied by the lubricating oil in the working chamber, and improve the volumetric efficiency of the compressor.

Referring to Fig. 2, in addition to the above arrangement mode, the oil inlet passage 4 has another possible arrangement as follows:

The oil inlet oil passage 4 is provided in plurality, and each of the oil inlet oil passages 4 collectively corresponds to the same tooth groove of the female rotor 2 or the male rotor 3.

Taking the same oil groove of the inlet oil passage 4 corresponding to the female rotor 2 as an example: when the oil inlet oil passage 4 is turned on, each of the oil inlet oil passages 4 simultaneously injects oil into the same tooth groove of the female rotor 2. Since the position of the oil inlet passage 4 is determined, the position of the tooth groove changes during the rotation of the female rotor 2, so that the atomized oil can be sprayed into each of the tooth grooves through the same group of oil inlet passages 4. To achieve sealing of the triangular leakage area in each compression chamber.

The following description will be made in three cases. The injection holes 41 of the oil inlet passage 4 are respectively located on the same spiral line, and the spiral line corresponds to the spiral line of the female rotor 2, the spiral line of the male rotor 3, and the spiral line. Two segments, one of the two segments corresponds to the spiral of the female rotor 2, and the other corresponds to the spiral of the male rotor 3.

In the first case, the inlet oil passage 4 is provided with a plurality of lines, and the center line of the injection holes 41 of each of the oil inlet passages 4 is located on the first spiral line. The first spiral is configured to coincide with the helix of the female rotor 2 during rotation of the female rotor 2.

The first spiral is used to coincide with the spiral of the female rotor 2, which means that the shape of the first spiral and the spiral of the female rotor 2 are matched so that the spiral of the female rotor 2 can be rotated during the rotation of the female rotor 2. At the same time, the first spiral is completely swept, and at this moment, the atomized oil sprayed from each of the injection holes 41 can simultaneously enter the same tooth groove of the female rotor 2.

Referring to Fig. 2, during the rotation of the female rotor 2, its spiral A is sequentially moved to a position where the first spiral B completely coincides. The spiral of the male rotor 3 described later is also similar to the first spiral.

In the above case, in order to facilitate the fuel injection, the first spiral is preferably disposed at a position to satisfy the following condition: the first spiral is disposed at a position that satisfies the following condition: the first spiral is used for the spiral with the female rotor 2 The lines coincide, and when the screw compressor is just beginning to exhaust, the first helix is located between the second and third slots of the female rotor 2 from the exhaust end of the screw compressor to the motor end.

The start of the exhaust of the screw compressor referred to herein means the moment immediately before the cogging is connected to the exhaust, that is, the timing at which the gas in the working chamber is about to communicate with the external exhaust port to discharge the compressed high-pressure gas. In the order of the number of cogs, the one of the slots that is to be exhausted is taken as the first slot.

In the above various setting modes, the required injection pressure is set so that the pressure of the rotor cavity is smaller than the pressure of the injection chamber, and the injection can be facilitated by the pressure difference to achieve the purpose of improving the volumetric efficiency. When the rotor is rotating, each working chamber sweeps through the spiral, that is, the injection has an effect on each compression chamber.

In the second case, the inlet oil passage 4 is provided with a plurality of strips, and the center line of the injection holes 41 of each of the oil inlet passages 4 is located on the first spiral line. The first spiral is configured to coincide with the helix of the male rotor 3 during the rotation of the male rotor 3.

The second case described above is similar to the first case except that the atomized oil is injected into the slots of the male rotor 2.

The first spiral is used to coincide with the spiral of the male rotor 3, which means that the shape of the first spiral and the spiral of the male rotor 3 are matched so that the spiral of the male rotor 3 can be rotated during the rotation of the male rotor 3. At the same time, the first spiral is completely swept, and at this moment, the atomized oil sprayed from each of the injection holes 41 can simultaneously enter the same tooth groove of the male rotor 3.

In the above case, in order to facilitate the fuel injection, the first spiral is preferably disposed at a position to satisfy the following condition: the first spiral is disposed at a position that satisfies the following condition: the first spiral is used for the spiral with the male rotor 3 The lines coincide, and when the screw compressor is just beginning to exhaust, the first spiral is located between the second and third slots of the male rotor 3 from the exhaust end of the screw compressor to the motor end.

The start of the exhaust of the screw compressor referred to herein means the moment immediately before the cogging is connected to the exhaust, that is, the timing at which the gas in the working chamber is about to communicate with the external exhaust port to discharge the compressed high-pressure gas. In the order of the number of cogs, the one of the slots that is to be exhausted is also used as the first slot.

In the third case, the inlet oil passage 4 is provided with a plurality of strips, and the center line of the injection holes 41 of each oil inlet passage 4 is located on a curve, and the curve includes a first spiral segment and a second spiral segment. The curve is configured such that during operation of the compressor, the first spiral segment is used to coincide with the helix of the female rotor 2 and the second spiral segment is used to coincide with the helix of the male rotor 3.

The first spiral segment is used to coincide with the spiral of the female rotor 2, which means that the shape of the spiral of the first spiral segment and the female rotor 2 is matched, so that the spiral wire of the female rotor 2 can be rotated during the rotation of the female rotor 2. At the same time, the first spiral section is completely swept, and at this moment, the atomized oil sprayed from each of the injection holes 41 can simultaneously enter the same tooth groove of the female rotor 2.

The second spiral segment is used to coincide with the spiral of the male rotor 3, which means that the shape of the spiral of the second spiral segment and the male rotor 3 is matched so that the spiral energy of the male rotor 3 during the rotation of the male rotor 3 At the same time, the second spiral section is completely swept, and at this moment, the atomized oil sprayed from each of the injection holes 41 can simultaneously enter the same tooth groove of the male rotor 3.

Similar to the position where the first spiral is arranged, in order to facilitate fuel injection, the position of the first spiral segment satisfies the following condition: the first spiral segment is used to coincide with the spiral of the female rotor 2, when the screw compressor is just beginning to exhaust The first spiral section is located between the second slot and the third slot of the female rotor 2 from the exhaust end of the screw compressor to the motor end.

Similar to the above, the order of the cogging is also determined by referring to the following manner: The start of the exhaust of the screw compressor referred to herein means the moment before the cogging is connected to the exhaust, that is, the gas in the working chamber is about to be discharged to the outside. The port is connected to a time at which the compressed high pressure gas is discharged. In the order of the number of cogs, the one of the slots that is to be exhausted is also used as the first slot.

Similar to the position where the second spiral is set as described above, in order to facilitate the fuel injection, the second spiral segment is disposed at a position that the second spiral segment is used to coincide with the spiral of the male rotor 3 when the screw compressor is just beginning to exhaust. The second spiral section is located between the second and third slots of the male rotor 3 from the exhaust end of the screw compressor to the motor end.

Similar to the above, the order of the cogging is also determined by referring to the following manner: The start of the exhaust of the screw compressor referred to herein means the moment before the cogging is connected to the exhaust, that is, the gas in the working chamber is about to be discharged to the outside. The port is connected to a time at which the compressed high pressure gas is discharged. In the order of the number of cogs, the one of the slots that is to be vented is also used as the first slot.

The required injection pressure is set so that the pressure of the rotor chamber is smaller than the pressure at the injection chamber, and the injection can be facilitated by the pressure difference to achieve the purpose of improving the volumetric efficiency. When the rotor is rotating, each tooth groove of the male rotor 3 sweeps through the first spiral segment, and each tooth groove of the female rotor 2 sweeps through the second spiral segment, that is, the injection oil has an effect on each compression cavity.

The embodiment of the present disclosure further provides a method for adjusting the volumetric efficiency of a screw compressor, which can be implemented by using the screw compressor provided in the above embodiment. The method includes the step of injecting atomized oil into a compression chamber formed by engagement of a female rotor and a male rotor of the screw compressor.

The atomized oil can form an oil film seal in the triangular leakage area of the screw compressor, effectively reducing the gas leakage amount in the triangular region of the screw compressor and improving the volumetric efficiency.

When the compressor runs at low speed, the leakage of gas through the leakage triangle increases. At this time, the solenoid valve can be opened, the oil passage connects the compressor oil tank 6 to the working chamber, and the Φ2 oil hole can atomize the lubricating oil. The lubricating oil forms a good effect on the oil film. The atomized lubricating oil is mixed with the refrigerant in the working chamber and forms a sealing oil film. The sealing oil film exists at the leakage triangle, which can reduce the gas leakage amount at the leakage triangle and improve the compressor. The actual amount of inhalation, thereby increasing the volumetric efficiency of the compressor. When the compressor is running at high speed, at this time, because the rotation speed is high, the working chamber is easy to form an oil film, and does not need too much lubricating oil. More lubricating oil enters the working chamber and will occupy a part of the volume. At this time, the solenoid valve can be passed. If the pulse is 1 stop 10, for example, 1 second is stopped for 10 seconds to reduce the fuel injection amount, reduce the volume occupied by the lubricating oil in the working chamber, and improve the volumetric efficiency of the compressor.

In the description of the present disclosure, it is to be understood that the terms "center", "longitudinal", "transverse", "front", "back", "left", "right", "vertical", "horizontal", The orientation or positional relationship of the "top", "bottom", "inside", "outside" and the like is based on the orientation or positional relationship shown in the drawings, and is merely for the convenience of describing the present disclosure and simplifying the description, rather than indicating or implying The device or component referred to must have a particular orientation, is constructed and operated in a particular orientation, and thus is not to be construed as limiting the scope of the disclosure.

It should be noted that the above embodiments are only used to illustrate the technical solutions of the present disclosure and are not to be construed as limiting thereof; although the present disclosure will be described in detail with reference to the preferred embodiments, those skilled in the art should understand that Modifications of the specific embodiments disclosed are intended to be equivalent to the equivalents of the technical features of the present disclosure.

Claims

A screw compressor comprising:

Body (1);

a female rotor (2) disposed inside the body (1);

a male rotor (3) disposed inside the body (1) and meshing with the female rotor (2), the female rotor (2) and the male rotor (3) meshing to form a compression chamber (11);

An atomizing structure is provided on the body (1) for injecting atomized oil into the compression chamber (11).
The screw compressor of claim 1 wherein said atomizing structure comprises:

An oil inlet passage (4) is provided at the body (1), and an end of the injection hole (41) of the oil inlet passage (4) is located at the end of the injection hole (41) and the female rotor (2) and/or the male rotor The cogging of (3) is in communication, and the oil inlet passage (4) is configured to be capable of atomizing oil.
The screw compressor of claim 2 wherein said atomizing structure further comprises:

A control unit (5) for controlling the conduction and the cut-off of the oil inlet passage (4).
A screw compressor according to claim 3, wherein said control member (5) is configured to continuously conduct said oil inlet passage (4) when said rotational speed of said screw compressor is lower than a given value When the rotational speed of the screw compressor is higher than or equal to a given value, the oil inlet passage (4) is periodically turned on.
The screw compressor according to claim 2, wherein said oil inlet passage (4) is provided in plurality, and each of said oil inlet passages (4) individually corresponds to said female rotor (2) or said male rotor (3) A cogging.
The screw compressor according to claim 2, wherein said oil inlet passage (4) is provided in plurality, and each of said oil inlet passages (4) collectively corresponds to said female rotor (2) or said male rotor (3) The same cogging.
The screw compressor according to claim 2, wherein said oil inlet passage (4) is provided in plurality, and a center line of said injection holes (41) of each of said oil inlet passages (4) is located at first Spiral line

The first spiral is configured to coincide with a helix of the female rotor (2) during rotation of the female rotor (2); or the first spiral is configured to be at the The rotor (3) is used to coincide with the spiral of the male rotor (3) during the rotation of the rotor (3).
The screw compressor according to claim 7, wherein the first spiral is disposed at a position that satisfies a condition that the first spiral is used to coincide with a helix of the female rotor (2) when When the screw compressor is just starting to exhaust, the first spiral is located at the second slot and the third tooth of the female rotor (2) starting from the exhaust end of the screw compressor to the motor end. Between the grooves; or, the first spiral is used to coincide with the spiral of the male rotor (3), the first spiral is located from the screw when the screw compressor is just starting to exhaust The exhaust end of the compressor is between the second slot and the third slot of the male rotor (3) starting at the motor end.
A screw compressor according to claim 2, wherein said oil inlet passage (4) is provided in plurality, and a center line of said injection holes (41) of each of said oil inlet passages (4) is located at a line In the curve, the curve includes a first spiral segment and a second spiral segment, the curve being configured to be used for the spiral of the female rotor (2) during operation of the compressor The lines coincide and the second spiral is used to coincide with the helix of the male rotor (3).
The screw compressor according to claim 9, wherein the set position of the first spiral segment satisfies a condition that the first spiral segment is used to coincide with a helix of the female rotor (2) when When the screw compressor is just starting to exhaust, the first spiral segment is located at the second slot and the third of the female rotor (2) starting from the exhaust end of the screw compressor to the motor end Between the slots.
The screw compressor according to claim 9, wherein the second spiral segment is disposed at a position that the second spiral segment is used to coincide with a helix of the male rotor (3) when When the screw compressor is just starting to exhaust, the second spiral segment is located at the second slot and the third of the male rotor (3) from the exhaust end of the screw compressor to the motor end Between the slots.
The screw compressor of claim 1 further comprising:

A return oil passage is provided in the body (1), and the return oil passage communicates with the female rotor (2) and/or the tooth groove of the male rotor (3).
The screw compressor according to claim 12, wherein said return oil passage is provided in plurality, and each of said return oil passages individually corresponds to teeth of said female rotor (2) or said male rotor (3) groove.
The screw compressor according to claim 2, wherein the injection hole (41) of the oil inlet passage (4) has an inner diameter of 1 mm to 3 mm.
The screw compressor according to claim 2, wherein the other end of the oil inlet passage (4) away from the injection hole (41) communicates with the oil groove (6) of the screw compressor.
A screw compressor according to claim 3, wherein said control member (5) comprises a valve, said valve being provided in said oil inlet passage (4).
An air conditioning apparatus comprising the screw compressor of claim 1.
A method for adjusting the volumetric efficiency of a screw compressor includes the following steps:

An atomized oil is sprayed into the compression chamber formed by the engagement of the female rotor and the male rotor of the screw compressor.
A method of adjusting a volumetric efficiency of a screw compressor according to claim 18, wherein

When the rotational speed of the screw compressor is lower than a given value, the atomizing oil is continuously injected into the compression chamber formed by the engagement of the female rotor and the male rotor; when the rotational speed of the screw compressor is higher than or equal to At a given value, atomized oil is periodically injected into the compression chamber formed by the engagement of the female rotor and the male rotor.