CN218093441U

CN218093441U - Two-stage compressor

Info

Publication number: CN218093441U
Application number: CN202221939806.3U
Authority: CN
Inventors: 周坤; 马升; 庄博; 康翔朝
Original assignee: Ningbo Baosi Energy Equipment Co Ltd
Current assignee: Ningbo Baosi Energy Equipment Co Ltd
Priority date: 2022-07-26
Filing date: 2022-07-26
Publication date: 2022-12-20
Anticipated expiration: 2032-07-26

Abstract

The utility model discloses a two-stage compressor, which comprises a low-pressure stage and a high-pressure stage; the low-voltage stage is connected with the high-voltage stage, and is characterized in that: the low-pressure stage is provided with a capacity adjusting assembly, and the high-pressure stage is provided with an internal volume ratio adjusting assembly. The double-stage compressor can change the output capacity and the exhaust end terminal pressure of the double-stage compressor, solves the problem that the process machine is difficult to start in a specific occasion, and can achieve the effects of improving the performance of a main machine, improving noise vibration and the like.

Description

Two-stage compressor

Technical Field

The utility model relates to a compressor technical field, more precisely relate to a doublestage compressor and air conditioning unit.

Background

In the conventional single-stage compressor, a capacity adjustment mechanism is used. Under some conditions, the unit needs to operate under a smaller load working condition, and the displacement of the sliding block of the compressor is controlled to change the capacity to meet the requirement.

However, in a two-stage compressor, the capacity is generally changed only by performing variable frequency modulation on the compressor. The inability to effectively regulate the internal volume ratio of a two-stage compressor results in over-compression and under-compression conditions in the compressor when the final compression pressure and discharge pressure are not equal, both of which result in additional energy loss and strong periodic discharge noise. In some specific occasions, the sucked gas has 1-2bar pressure, the pressure of the sucked gas is high, and an air inlet valve is not generally arranged, so that the starting difficulty is caused, and the conditions are specifically represented by the conditions of overcurrent, frequency converter alarm, copper wire heating and the like.

SUMMERY OF THE UTILITY MODEL

The to-be-solved technical problem of the utility model is to provide a double stage compressor, this double stage compressor can change double stage compressor's output capacity and row end pressure, and it is difficult to solve the aircraft engine start when specific occasion to can reach and improve the host computer performance, improve effects such as noise vibration.

The technical solution of the utility model is to provide a two-stage compressor with the following structure, which comprises a low-pressure stage and a high-pressure stage; the low-pressure stage is connected with the high-pressure stage, a capacity adjusting assembly is arranged on the low-pressure stage, and an internal volume ratio adjusting assembly is arranged on the high-pressure stage.

After the structure more than adopting, the utility model discloses a two-stage compressor compares with prior art, has following advantage:

because the utility model discloses a two-stage compressor includes low-pressure stage and high-pressure stage, the low-pressure stage on be provided with capacity adjusting part, the high-pressure stage on be provided with interior volume ratio adjusting part. The combined structure of the capacity regulating slide valve and the internal volume ratio regulating slide valve is designed in the double-stage screw compressor, so that the output capacity and the exhaust end final pressure of the double-stage compressor can be changed, the problem that the process machine is difficult to start in a specific occasion is solved, and the effects of improving the performance of a main machine, improving noise vibration and the like can be achieved.

As an improvement, the capacity regulating assembly comprises a first driving assembly and a capacity regulating slide valve, and the first driving assembly is used for driving the capacity regulating slide valve to work; the capacity regulating slide valve is arranged at the discharge end of the low-pressure stage and is used for regulating the gas output capacity of the low-pressure stage. During operation, according to the requirement of actual working conditions, the size of the bypass hole is changed through the left-right sliding of the capacity adjusting mechanism, so that the gas at the side of the bypass hole at the air inlet end is released without compression, and the part of gas returns to the air suction port of the compressor again. Since the compressor does not actually work on this portion of the gas, nor does its temperature rise, it changes the aspect ratio of its rotor to adjust the output volume of the low pressure stage.

As an improvement, the internal volume ratio adjusting assembly comprises a second driving assembly and an internal volume ratio adjusting slide valve, and the second driving assembly is used for driving the internal volume ratio adjusting slide valve to work; the internal volume ratio adjusting slide valve is arranged at the exhaust port of the high-pressure stage and used for adjusting the output position of the exhaust port of the high-pressure stage. After the structure is adopted, the final pressure and the exhaust pressure are not consistent in the operation process, so that the host does more work, the performance of the host is influenced, and overlarge noise and vibration are caused. However, the high-pressure stage volume ratio adjusting mechanism can adjust the size of a radial discharge port of a high-pressure stage compression cavity through left and right sliding to change the internal volume ratio, so that the final pressure is matched with the exhaust pressure, and the effects of reducing energy consumption, noise and the like are achieved.

As an improvement, a first-stage rotor set is arranged in the low-pressure stage, and a second-stage rotor set is arranged in the high-pressure stage; the outer diameter of the first-stage male rotor of the first-stage rotor set is larger than that of the second-stage male rotor of the second-stage rotor set.

As an improvement, the length of the first-stage male rotor of the first-stage rotor set is larger than that of the second-stage male rotor of the second-stage rotor set.

As an improvement, the low-voltage stage and the high-voltage stage are in a series structure which is arranged up and down, and the low-voltage stage is positioned in the horizontal direction of the high-voltage stage; the driving mechanism is in transmission connection with the first-stage rotor set through a first gear assembly, and the first-stage rotor set is in transmission connection with the second-stage rotor set through a second gear assembly.

As an improvement, the low-voltage stage and the high-voltage stage are in a parallel structure which is arranged up and down, and the low-voltage stage is positioned above the high-voltage stage; the driving mechanism is in transmission connection with the first-stage rotor set and the second-stage rotor set through a third gear assembly.

Drawings

Fig. 1 is a schematic structural diagram of a two-stage compressor according to a first embodiment of the present invention.

Fig. 2 is a schematic structural diagram of a two-stage compressor according to a first embodiment of the present invention, before and after slide valve adjustment.

Fig. 3 is a schematic power consumption diagram of the two-stage compressor according to the first embodiment of the present invention when the internal pressure and the external pressure are matched.

Fig. 4 is a schematic power consumption diagram of the dual-stage compressor according to the first embodiment of the present invention when the internal pressure and the external pressure are under-compressed.

Fig. 5 is a schematic diagram of power consumption of the two-stage compressor according to the first embodiment of the present invention when the internal pressure and the external pressure are over-compressed.

Fig. 6 is a schematic structural diagram of a two-stage compressor according to a second embodiment of the present invention.

Shown in the figure:

example one

1. The device comprises a low-pressure stage 101, a first-stage rotor set 2, a high-pressure stage 201, a second-stage rotor set 3, a driving shaft 4, a first gear set 5, a second gear set 6, a first driving assembly 7, a capacity adjusting slide valve 8, a second driving assembly 9 and an internal volume ratio adjusting slide valve;

example two

1', low pressure stage, 101', primary rotor set, 2', high pressure stage, 201', secondary rotor set, 3', drive shaft, 4', third gear set.

Detailed Description

For a better understanding of the present application, various aspects of the present application will be described in more detail with reference to the accompanying drawings. It should be understood that the detailed description is merely illustrative of exemplary embodiments of the present application and does not limit the scope of the present application in any way. Like reference numerals refer to like elements throughout the specification.

In the drawings, the thickness, size, and shape of an object have been slightly exaggerated for convenience of explanation. The figures are purely diagrammatic and not drawn to scale.

It will be further understood that the terms "comprises," "comprising," "includes," "including," "has," "having," "contains," "including," and/or "containing," when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof.

Example one

As shown in fig. 1 and 2, the present embodiment discloses a two-stage compressor, which includes a low-pressure stage 1, a high-pressure stage, and a driving mechanism. The low-pressure stage 1 is internally provided with a first-stage rotor set 101, and the high-pressure stage 2 is internally provided with a second-stage rotor set 201. The low-voltage stage 1 and the high-voltage stage 2 are in a series structure which is arranged up and down, and the low-voltage stage 1 is positioned in the horizontal direction of the high-voltage stage 2. The drive mechanism through 4 transmission connections with one-level rotor group 101 of first gear train, promptly drive mechanism's drive shaft 3 on be equipped with drive gear, 4 first gear train include first driven gear and second driven gear, first driven gear connect the inlet end of one-level male rotor, second driven gear connect the inlet end of one-level female rotor, drive gear with first driven gear meshing, first driven gear with second driven gear meshing, one-level male rotor with one-level female rotor meshing. First-level rotor set 101 and second-level rotor set 201 between be connected through 5 transmission of second gear set, 5 of second gear set include driving gear, third driven gear and fourth driven gear, the driving gear connect the exhaust end of first-level male rotor, third driven gear connect the inlet end of second-level male rotor, fourth driven gear connect the inlet end of second-level female rotor. The driving gear is meshed with the third driven gear, the third driven gear is meshed with the fourth driven gear, and the secondary male rotor is meshed with the secondary female rotor. In operation, the drive shaft 3 drives the primary male rotor to rotate, and the primary male rotor drives the primary female rotor to rotate; meanwhile, the first-stage male rotor drives the second-stage male rotor to rotate, and the second-stage male rotor drives the second-stage female rotor to rotate.

The low-pressure stage 1 is provided with a capacity adjusting assembly, the capacity adjusting assembly comprises a first driving assembly 6 and a capacity adjusting slide valve 7, and the first driving assembly 6 is used for driving the capacity adjusting slide valve 7 to work. The capacity regulating slide valve 7 is provided at the discharge end of the low pressure stage 1, i.e., is installed on the sidewall of the compression chamber of the low pressure stage 1, and the capacity regulating slide valve 7 is used to regulate the gas output volume of the low pressure stage 1. The screw compressor volumetric flow is calculated as follows:

1 theoretical volumetric flow

Theoretical volumetric flow q of a screw compressor _Vt The sum of the tooth volumes that the rotor rotates per unit of time depends only on the geometry and the speed of the compressor. If let λ = L/D ₁ Then, then

Towel z ₁ -the number of teeth of the male rotor;

n-the rotational speed of the male rotor;

λ -rotor length to diameter ratio;

D _t the outer diameter of the male rotor.

2 actual volume flow

The actual volume flow of the screw compressor is converted to the actual volume flow v of the suction state by taking into account the volumetric efficiency eta _V Then, then

It can be concluded that changes in rotor aspect ratio affect compressor volumetric flow. Further illustrating that the volume flow of a stage can be adjusted by axial movement of the capacity-adjusting slide valve.

The principle that the volume flow of the screw compressor is adjusted by the capacity adjusting slide valve is based on the working process characteristics of the screw compressor. As shown in fig. 2, in the screw compressor, the pressure of the gas to be compressed gradually increases along the axial direction of the rotor as the rotor rotates, and gradually moves from the suction end to the discharge end of the compressor at a spatial position. When the rotors begin to mesh and attempt to increase the gas pressure, as shown in figure 2b, behind the high pressure side opening in the body, some of the gas is bypassed through the opening, obviously depending on the length of the opening. The slide valve can move in any direction according to the requirements of a control system, the driving mode of the slide valve is various, the most common mode adopts a hydraulic cylinder mode, and an oil circuit system of the compressor provides required oil pressure.

The internal volume ratio adjusting assembly comprises a second driving assembly 8 and an internal volume ratio adjusting slide valve 9, and the second driving assembly 8 is used for driving the internal volume ratio adjusting slide valve 9 to work. The internal volume ratio regulating slide valve 9 is arranged at the exhaust port of the high pressure stage 2, namely, is arranged on the side wall of the compression cavity of the high pressure stage 2, and the internal volume ratio regulating slide valve 9 is used for regulating the output position of the exhaust port of the high pressure stage 2.

To explain in detail how the internal volume ratio regulating slide valve 9 can achieve the energy saving effect, schematic diagrams 3 to 5 are given to express the operation of the compressor as if.

The outer diameter of the first-stage male rotor of the first-stage rotor set 101 is larger than that of the second-stage male rotor of the second-stage rotor set 201. The length of the first-stage male rotor of the first-stage rotor set 101 is greater than that of the second-stage male rotor of the second-stage rotor set 201.

Example two

As shown in fig. 6, the present embodiment discloses a two-stage compressor, which has the following differences from the first embodiment: in this embodiment, the low-voltage stage 1 'and the high-voltage stage 2' are arranged in parallel, and the low-voltage stage 1 'is located above the high-voltage stage 2'. The driving mechanism is in transmission connection with the first-stage rotor set 101' and the second-stage rotor set 201' through a third gear set 4', namely a driving gear is arranged on a driving shaft 3' of the driving mechanism, and the third gear set 4' comprises a fifth driven gear, a sixth driven gear, a seventh driven gear and an eighth driven gear. The fifth driven gear is connected with the air inlet end of the first-stage male rotor, the sixth driven gear is connected with the air inlet end of the first-stage female rotor, the fifth driven gear is meshed with the driving gear, the fifth driven gear is meshed with the sixth driven gear, and the first-stage male rotor is meshed with the first-stage female rotor. The seventh driven gear is connected with the air inlet end of the secondary male rotor, the eighth driven gear is connected with the air inlet end of the secondary female rotor, the seventh driven gear is meshed with the driving gear, the seventh driven gear is meshed with the eighth driven gear, and the secondary male rotor is meshed with the secondary female rotor.

Claims

1. A two-stage compressor comprises a low-pressure stage and a high-pressure stage; the low-voltage stage is connected with the high-voltage stage, and is characterized in that: the low-pressure stage is provided with a capacity adjusting assembly, and the high-pressure stage is provided with an internal volume ratio adjusting assembly.

2. The two-stage compressor of claim 1, wherein: the capacity adjusting assembly comprises a first driving mechanism and a capacity adjusting slide valve, and the first driving mechanism is used for driving the capacity adjusting slide valve to work; the volume adjusting slide valve is arranged at the discharge end of the low-pressure stage and is used for adjusting the gas output volume of the low-pressure stage.

3. The two-stage compressor of claim 1, wherein: the internal volume ratio adjusting assembly comprises a second driving mechanism and an internal volume ratio adjusting slide valve, and the second driving mechanism is used for driving the internal volume ratio adjusting slide valve to work; the internal volume ratio adjusting slide valve is arranged at the exhaust port of the high-pressure stage and used for adjusting the output position of the exhaust port of the high-pressure stage.

4. The two-stage compressor according to any one of claims 1 to 3, wherein: a first-stage rotor set is arranged in the low-pressure stage, and a second-stage rotor set is arranged in the high-pressure stage; the outer diameter of the first-stage male rotor of the first-stage rotor set is larger than that of the second-stage male rotor of the second-stage rotor set.

5. The two-stage compressor of claim 4, wherein: the length of the first-stage male rotor of the first-stage rotor set is greater than that of the second-stage male rotor of the second-stage rotor set.

6. The two-stage compressor of claim 5, wherein: the low-voltage stage and the high-voltage stage are in a series structure which is arranged up and down, and the low-voltage stage is positioned in the horizontal direction of the high-voltage stage; the driving mechanism is in transmission connection with the first-stage rotor set through a first gear assembly, and the first-stage rotor set is in transmission connection with the second-stage rotor set through a second gear assembly.

7. The two-stage compressor of claim 5, wherein: the low-voltage stage and the high-voltage stage are in a parallel structure which is arranged up and down, and the low-voltage stage is positioned above the high-voltage stage; the driving mechanism is in transmission connection with the first-stage rotor set and the second-stage rotor set through a third gear assembly.