A two-stage compressor and air conditioning system

Abstract

The utility model discloses a kind of two-stage compressor and air conditioning system, the two-stage compressor includes suction end cover, further include the screw compressor for the low-pressure stage part of the two-stage compressor, and the sliding vane compressor for the high-pressure stage part of the two-stage compressor;The screw compressor and the sliding vane compressor are connected in series in the rear end of the suction end cover.Compared with prior art, the utility model uses the two-stage compressor of low-pressure stage for screw compressor, high-pressure stage for sliding vane compressor, compared with traditional two-stage screw compressor can be applied to lower exhaust capacity, and with smaller volume and lower cost, higher operating stability.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a two-stage compressor and air conditioning system. Background Technology

[0002] Using a two-stage compressor can significantly improve compressor efficiency, so two-stage compressors are frequently used in actual production.

[0003] Currently, most two-stage compressors use two screw compressors connected in series, which is called a two-stage screw compressor. However, two-stage screw compressors have the following disadvantages:

[0004] 1. Complex structure: Two-stage screw compressors contain two-stage screw structures, with a significantly larger number of parts and a complex structure, which can easily lead to problems with difficult maintenance;

[0005] 2. Suitable for high displacement and high pressure applications: The two-stage screw compressor makes the compressor particularly suitable for high displacement and high pressure conditions;

[0006] 3. Larger size: The use of a two-stage screw compressor means that the low-pressure stage screw components and the high-pressure stage screw components are connected in series, resulting in a significantly larger overall size of the compressor;

[0007] 4. High cost: Due to the two-stage screw structure, the cost is significantly increased, resulting in a low cost-performance ratio.

[0008] Therefore, how to design a two-stage compressor and air conditioning system that can reduce exhaust volume, size, and cost while ensuring compressor efficiency, so as to adapt to more operating conditions, is a technical problem that the industry urgently needs to solve. Utility Model Content

[0009] In view of the shortcomings of existing two-stage compressors, this utility model proposes a two-stage compressor and air conditioning system.

[0010] The technical solution of this utility model is to propose a two-stage compressor, including an intake end cover 1, a screw compressor 6 serving as the low-pressure stage of the two-stage compressor, and a vane compressor 9 serving as the high-pressure stage of the two-stage compressor.

[0011] The screw compressor 6 and the vane compressor 9 are connected in series at the rear end of the suction end cover 1.

[0012] Furthermore, the screw compressor 6 includes a low-pressure stage male rotor 4 and a low-pressure stage female rotor 5, and the low-pressure stage male rotor 4 is connected to a first gear 8;

[0013] The vane compressor 9 includes a compression shaft 10, and the compression shaft 10 is connected to a second gear 7;

[0014] The first gear 8 rotates under the drive of the low-pressure stage male rotor 4, and the first gear 8 is used to drive the second gear 7 to rotate, and the second gear 7 is used to drive the compression shaft 10 to rotate.

[0015] Furthermore, the first gear 8 is meshed with the second gear 7, and the number of gears in the first gear 8 is less than the number of gears in the second gear 7.

[0016] Furthermore, the first gear 8 and the second gear 7 are coaxially arranged, and the number of gears in the first gear 8 is greater than the number of gears in the second gear 7.

[0017] Furthermore, it also includes a motor disposed within the intake end cover 1, the motor having a motor stator 2 and a motor rotor 3;

[0018] The motor rotor 3 is connected to the low-voltage stage male rotor 4 and drives the low-voltage stage male rotor 4 to rotate.

[0019] Furthermore, it also includes a plurality of vanes 11 disposed within the vane compressor 9, and the two ends of the vanes 11 abut against the inner wall of the vane compressor 9;

[0020] When the compression shaft 10 rotates, the plurality of vanes 11 and the inner wall of the vane compressor 9 form a plurality of chambers with periodically changing volumes.

[0021] Furthermore, it also includes an air intake 12 and an exhaust port 13;

[0022] The air intake 12 is located on the air intake end cover 1, and the exhaust port 13 is located on the housing of the vane compressor 9.

[0023] Furthermore, the intake capacity of the screw compressor 6 is 2000m³. 3 / h, the suction capacity of the sliding vane compressor 9 is 500m³ / h. 3 / h.

[0024] Furthermore, the intake capacity of the screw compressor 6 is 1000m³. 3 / h, the suction capacity of the sliding vane compressor 9 is 100m³ / h. 3 / h.

[0025] Furthermore, the screw compressor 6 has a rotational speed of 1500 rpm to 6000 rpm, and the vane compressor 9 has a rotational speed of 500 rpm to 1500 rpm.

[0026] This utility model also proposes an air conditioning system having the above-mentioned two-stage compressor.

[0027] Compared with the prior art, the present invention has at least the following beneficial effects:

[0028] 1. This utility model is a two-stage compressor, which has higher efficiency compared to the traditional compressor structure;

[0029] 2. The high-pressure stage of this utility model adopts a vane compressor, which, compared with the high-pressure stage of a two-stage screw compressor, is designed to handle lower discharge volumes.

[0030] 3. The high-pressure stage of this utility model adopts a vane compressor, which has a smaller size and lower cost compared to the high-pressure stage of a two-stage screw compressor.

[0031] 4. The high-pressure stage of this utility model adopts a vane compressor, which has weaker airflow pulsation compared to the high-pressure stage of a two-stage screw compressor, making the operation of the two-stage compressor more stable. Attached Figure Description

[0032] To more clearly illustrate the technical solutions in the embodiments of this utility model, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0033] Figure 1 This is a schematic diagram of the structure of a two-stage screw compressor in the prior art;

[0034] Figure 2 This is a schematic diagram of the structure of the two-stage compressor in this utility model;

[0035] Figure 3 This is a schematic diagram of the internal structure of the sliding vane compressor in this utility model;

[0036] Wherein, 1 is the intake end cap;

[0037] 2 represents the motor stator;

[0038] 3 represents the motor rotor;

[0039] 4 is the low-pressure stage male rotor;

[0040] 5 is the low-pressure stage female rotor;

[0041] 6 is a screw compressor;

[0042] 7 represents the second gear;

[0043] 8 represents the first gear;

[0044] 9 is a sliding vane compressor;

[0045] 10 is the compression axis;

[0046] 11 is the slider;

[0047] 12 is the air intake;

[0048] 13 is the exhaust port. Detailed Implementation

[0049] To make the technical problems, technical solutions, and beneficial effects of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present utility model and are not intended to limit the present utility model.

[0050] Therefore, a feature pointed out in this specification is used to describe one feature of one embodiment of the present invention, and does not imply that every embodiment of the present invention must have the described feature. Furthermore, it should be noted that this specification describes many features. Although certain features may be combined to illustrate possible system designs, these features may also be used in other combinations not explicitly stated. Therefore, unless otherwise stated, the described combinations are not intended to be limiting.

[0051] The principle and structure of this utility model will be described in detail below with reference to the accompanying drawings and embodiments.

[0052] Currently, most two-stage compressors use two screw compressors connected in series, which is called a two-stage screw compressor. However, two-stage screw compressors have the following disadvantages:

[0053] 1. Complex structure: Two-stage screw compressors contain two-stage screw structures, with a significantly larger number of parts and a complex structure, which can easily lead to problems with difficult maintenance;

[0054] 2. Suitable for high displacement and high pressure applications: The two-stage screw compressor makes the compressor particularly suitable for high displacement and high pressure conditions;

[0055] 3. Larger size: The use of a two-stage screw compressor means that the low-pressure stage screw components and the high-pressure stage screw components are connected in series, resulting in a significantly larger overall size of the compressor;

[0056] 4. High cost: Due to the two-stage screw structure, the cost is significantly increased, resulting in a low cost-performance ratio.

[0057] To address the aforementioned problems, the design concept of this utility model is to propose a two-stage compressor, which changes the high-pressure stage from the original screw compressor to a vane compressor. Compared with screw compressors, vane compressors are suitable for lower displacement, have smaller size, lower cost, and weaker gas pulsation, thus effectively solving the problems existing in the prior art.

[0058] Please see Figure 2 Based on the above design concept, the two-stage compressor proposed in this utility model includes an intake end cover 1, a screw compressor 6 serving as the low-pressure stage of the two-stage compressor, and a vane compressor 9 serving as the high-pressure stage of the two-stage compressor.

[0059] The screw compressor 6 and the vane compressor 9 are connected in series at the rear end of the suction end cover 1.

[0060] As can be seen from the above configuration, this utility model mainly consists of three parts: the first part is the intake end cover 1, which is equipped with a motor; the second part is the screw compressor 6 of the low-pressure stage; and the third part is the vane compressor 9 of the high-pressure stage.

[0061] Please see Figure 1 A traditional two-stage screw compressor also consists of three parts: the first part is the suction end cover, which houses the motor; the second part is the low-pressure stage screw compressor; and the third part is the high-pressure stage screw compressor.

[0062] As can be seen from the above comparison, the main improvement of this utility model compared with the traditional two-stage screw compressor lies in the high-pressure stage, which is to change the traditional screw compressor into a vane compressor.

[0063] Here, the vane compressor 9 is suitable for lower discharge volumes compared to the screw compressor, and also has advantages such as small size, low cost, and high reliability. Therefore, by replacing the screw compressor in the high-pressure stage with the vane compressor 9 in this invention, the resulting two-stage compressor also has the aforementioned advantages of lower discharge volume, smaller size, lower cost, and higher reliability compared to a traditional two-stage screw compressor.

[0064] Please see Figure 1 In a traditional two-stage screw compressor, both the low-pressure stage and the high-pressure stage are screw compressors, and the two compressors rotate at the same speed. Therefore, in the design of a traditional two-stage screw compressor, the low-pressure stage male rotor of the screw compressor in the low-pressure stage is directly coaxially set with the high-pressure stage male rotor of the screw compressor in the high-pressure stage. This ensures that the screw compressors in the low-pressure stage and the high-pressure stage rotate at the same speed.

[0065] Please see Figure 2 In the two-stage screw compressor of this utility model, the low-pressure stage is a screw compressor 6 and the high-pressure stage is a vane compressor 9. The screw compressor 6 and the vane compressor 9 generally have different speeds. Therefore, the screw compressor 6 and the vane compressor 9 cannot be connected by the coaxial arrangement mentioned above. The connection structure needs to be improved so that the screw compressor 6 can drive the vane compressor 9 and meet the different speeds of the two.

[0066] Based on this problem, the improvement of the two-stage compressor proposed in this utility model is as follows:

[0067] The screw compressor 6 includes a low-pressure stage male rotor 4 and a low-pressure stage female rotor 5, and the low-pressure stage male rotor 4 is connected to a first gear 8;

[0068] The vane compressor 9 includes a compression shaft 10, and the compression shaft 10 is connected to a second gear 7;

[0069] The first gear 8 rotates under the drive of the low-pressure stage male rotor 4, and the first gear 8 is used to drive the second gear 7 to rotate, and the second gear 7 is used to drive the compression shaft 10 to rotate.

[0070] Here, the first gear 8 is connected to the low-pressure stage male rotor 4, so the angular velocity of the first gear 8 is the same as the angular velocity of the low-pressure stage male rotor 4.

[0071] Similarly, the second gear 7 is connected to the compression shaft 10, so the angular velocity of the second gear 7 is the same as the angular velocity of the compression shaft 10.

[0072] Since the first gear 8 is used to drive the second gear 7 to rotate, they can be driven by meshing. Therefore, when the first gear 8 and the second gear 7 rotate, the actual number of gears they pass through should be exactly the same.

[0073] The above settings allow the rotational speed of the low-pressure stage male rotor 4 to differ from that of the compression shaft 10, thus satisfying the different rotational speeds of the screw compressor 6 and the vane compressor 9. The specific principle analysis is as follows:

[0074] Since the low-pressure stage male rotor 4 drives the first gear 8 to move together, the speed of the first gear 8 is the same as the speed of the low-pressure stage male rotor 4. Since the speed is proportional to the number of revolutions of the low-pressure stage male rotor 4 and the first gear 8, let's assume that the low-pressure stage male rotor 4 rotates m revolutions, and the first gear 8 will also rotate m revolutions accordingly.

[0075] Let the number of gears in the first gear 8 be p, and the number of gears in the second gear 7 be q. Since the first gear 8 is used to drive the second gear 7 to rotate, the number of gears they pass through should be the same. When the first gear 8 rotates m times, the actual number of gears it passes through is mp.

[0076] Let n be the number of rotations of the second gear 7, and nq be the number of gears it actually passes through. The first gear 8 and the second gear 7 pass through the same number of gears, so mp = nq should be satisfied.

[0077] Dividing it further, we get m:n = q:p;

[0078] That is, the number of rotations of the first gear 8 and the second gear 7 is inversely proportional to the number of their gears. Since the rotation speed of the first gear 8 is the same as the rotation speed of the low-pressure stage male rotor 4, and the rotation speed of the second gear 7 is the same as the rotation speed of the compression shaft 10, the rotation speed of the low-pressure stage male rotor 4 and the rotation speed of the compression shaft 10 are also inversely proportional to the number of their connected first gear 8 and second gear 7.

[0079] Therefore, with the above settings, the speed of the low-pressure stage male rotor 4 and the compression shaft 10 can be adjusted according to the number of gears of the first gear 8 and the second gear 7. That is, the speed of the screw compressor 6 and the vane compressor 9 can be adjusted accordingly, so that the screw compressor 6 in the low-pressure stage and the vane compressor 10 in the high-pressure stage form a speed difference, ensuring the normal operation of the two-stage compressor.

[0080] In practical applications, the rotational speed of the screw compressor 6 is generally greater than that of the vane compressor 9. Therefore, after setting the first gear 8 and the second gear 7, it is necessary to satisfy the relationship that the rotational speed of the screw compressor 6 is greater than that of the vane compressor 9. As can be seen from the previous analysis, the rotational speed of the screw compressor 6 and the rotational speed of the vane compressor 9 are inversely proportional to the number of gears of the first gear 8 and the second gear 7 connected to it. Therefore, the number of gears of the first gear 8 can be set to be less than the number of gears of the second gear 7, which can satisfy the relationship that the rotational speed of the screw compressor 6 is greater than that of the vane compressor 9, and ensure the normal operation of the two-stage compressor.

[0081] Therefore, in this invention, when the first gear 8 and the second gear 7 are meshed, the number of gears in the first gear 8 is less than the number of gears in the second gear 7.

[0082] In addition, in other embodiments of this utility model, the first gear 8 and the second gear 7 can also be arranged coaxially. In this case, the number of gears of the first gear 8 needs to be set to be more than the number of gears of the second gear 7. However, under this setting, when the first gear 8 is driven to rotate by the low-pressure stage male rotor 4, it is necessary to ensure that the number of gears passed by the low-pressure stage male rotor 4 and the first gear 8 is the same. Similarly, when the compression shaft 10 is driven to rotate by the second gear 7, it is also necessary to ensure that the number of gears passed by the second gear 7 and the compression shaft is the same.

[0083] Since the first gear 8 and the second gear 7 are coaxially arranged, the rotational speeds of the first gear 8 and the second gear 7 must be the same. That is, in the same time period, the number of rotations of the first gear 8 is the same as the number of rotations of the second gear 7. Here, we will still use the number of gears of the first gear 8 as p and the number of gears of the second gear 7 as q for explanation.

[0084] Assuming that the first gear 8 and the second gear 7 rotate together for m revolutions, since the first gear 8 is driven by the low-pressure stage male rotor 4, the actual number of gears that the low-pressure stage male rotor 4 passes through is mp. Similarly, since the second gear 7 is used to drive the compression shaft 10 to rotate, the actual number of gears that the compression shaft 10 passes through is mq.

[0085] Here, we will explain the process by taking the low-pressure stage male rotor 4 and the compression shaft 10 as having the same number of gears that they pass through in one revolution, both of which are z, and the number of revolutions of the low-pressure stage male rotor 4 as x and the number of revolutions of the compression shaft 10 as y.

[0086] At this time, the actual number of gears that the low-pressure stage male rotor 4 passes through satisfies xz = mp, and its division can be obtained as xz / p = m;

[0087] The actual number of gears that the compression shaft 10 passes through satisfies yz=mq, and its division can be obtained as yz / q=m;

[0088] Combining the above equations, we have xz / p = yz / q, which means x:y = p:q;

[0089] Since the rotational speed of the low-pressure stage male rotor 4 and the compression shaft 10 is proportional to the number of revolutions they make in the same time period, it can be concluded that the rotational speed of the low-pressure stage male rotor 4 is proportional to the rotational speed of the compression shaft 10 and the number of gears of the first gear 8 and the second gear 7 connected to it.

[0090] Therefore, with the above settings, the speed of the low-pressure stage male rotor 4 and the compression shaft 10 can be adjusted according to the number of gears of the first gear 8 and the second gear 7. That is, the speed of the screw compressor 6 and the vane compressor 9 can be adjusted accordingly, so that the screw compressor 6 in the low-pressure stage and the vane compressor 10 in the high-pressure stage form a speed difference, ensuring the normal operation of the two-stage compressor.

[0091] In practical applications, the rotational speed of the screw compressor 6 is generally greater than that of the vane compressor 9. Therefore, after setting the first gear 8 and the second gear 7, it is necessary to satisfy the relationship that the rotational speed of the screw compressor 6 is greater than that of the vane compressor 9. As can be seen from the previous analysis, the rotational speed of the screw compressor 6 and the rotational speed of the vane compressor 9 are directly proportional to the number of gears of the first gear 8 and the second gear 7 connected to it. Therefore, the number of gears of the first gear 8 can be set to be greater than the number of gears of the second gear 7, which can satisfy the relationship that the rotational speed of the screw compressor 6 is greater than that of the vane compressor 9, and ensure the normal operation of the two-stage compressor.

[0092] Therefore, in this invention, when the first gear 8 and the second gear 7 are coaxially arranged, the number of gears in the first gear 8 is greater than the number of gears in the second gear 7.

[0093] The structure of this utility model can also be implemented in other ways, such as coaxial direct drive, where the low-pressure stage male rotor 4 is driven by a motor, and the vane compressor 9 and the low-pressure stage female rotor 5 with more gears and lower speed are coaxially arranged. Alternatively, the vane compressor can be directly driven by a motor, and the low-pressure stage male rotor 4 of the screw compressor 6 can be driven by a speed-increasing gear.

[0094] From the above logical relationship, it can be seen that the screw compressor 6 drives the first gear 8 to rotate, the first gear 8 drives the second gear 7 to rotate, and the second gear 7 drives the vane compressor 8 to rotate. The arrangement of the first gear 8 and the second gear 7 actually discloses the relevant configuration of the screw compressor 6 driving the vane compressor 8 to rotate. However, in actual configuration, it is also necessary to provide a corresponding power device for the screw compressor 6 to make it rotate.

[0095] To achieve the above objectives, the present invention is configured as follows:

[0096] The two-stage compressor also includes a motor disposed within the suction end cover 1, the motor having a motor stator 2 and a motor rotor 3;

[0097] The motor rotor 3 is connected to the low-voltage stage male rotor 4 and is used to drive the low-voltage stage male rotor 4 to rotate.

[0098] The motor is a conventional component in this field, and its rotation can be controlled by power supply. In this invention, the motor is used as a power component to drive the low-pressure stage male rotor 4, which can then be used to drive the rotation of the screw compressor 6, and in turn drive the rotation of the vane compressor 9, thereby realizing the operation of the entire two-stage compressor.

[0099] This part corresponds to the three parts mentioned above. The first part is the suction end cover 1, which is the part that provides power to the screw compressor 6 through the motor. The second part is the screw compressor 6 in the low-pressure stage, which is used to perform the first compression and drive the vane compressor 9 to rotate for the second compression.

[0100] Since the exhaust is ultimately compressed by the rotation of the vane compressor 9, this design has the advantages of a vane compressor, namely, compared to the screw compressor 6, it is suitable for lower exhaust volumes, has a smaller size, lower cost, and weaker airflow pulsation.

[0101] The above describes the overall driving principle of this utility model. As can be seen from the above description, the main improvement of this utility model lies in the setting of the sliding vane compressor 9. The working principle of the sliding vane compressor 9 will be explained below:

[0102] Please see Figure 3 The sliding vane compressor 9 proposed in this utility model is provided with a plurality of sliding vanes 11, and the two ends of the sliding vanes 11 abut against the inner wall of the sliding vane compressor 9.

[0103] When the compression shaft 10 rotates, multiple vanes 11 and the inner wall of the vane compressor 9 form multiple chambers with periodically changing volumes.

[0104] Specifically, the principle of the vane compressor 9 is that the vane is the main shaft of the compressor 9, that is, the compression shaft 10 and the inner wall of the housing of the vane are eccentric circles. When the compression shaft 10 rotates, multiple vanes 11 will extend and retract in the radial groove of the compression shaft 10. At the same time, the top of the vane 11 always presses against the inner wall of the vane compressor 9, forming several chambers with a periodic change in volume that continuously "increases" - "maximum" - "decreases" - "minimum" - "increases".

[0105] The first half of "maximum" or "decreasing" indicates the end of inhalation; the second half of "decreasing" or "minimum" indicates the end of compression and the beginning of exhalation.

[0106] In other words, by setting up the sliding vane 11 and the compression shaft 10, this utility model cooperates with the housing of the sliding vane compressor 9 to realize the chamber that changes periodically from "larger" to "maximum" to "smaller" to "minimum" to "larger", thereby ensuring the normal working logic of the sliding vane compressor 9.

[0107] Furthermore, this utility model also includes an air intake 12 and an exhaust port 13;

[0108] Here, the air intake 12 is located on the air intake end cover 1, and the exhaust port 13 is located on the housing of the vane compressor 9.

[0109] For a compressor, the above-mentioned intake port 12 and exhaust port 13 are necessary, used to draw in gas and discharge compressed gas, respectively. Since the present invention is a two-stage compressor, the intake port 12 needs to be set at the place where the gas first enters and begins to compress, and the exhaust port 13 needs to be set at the place where the two gas compressions are finally completed. That is, the intake port 12 needs to be set on the intake end cover 1, and the exhaust port 13 needs to be set on the housing of the vane compressor 9.

[0110] In other words, by setting the above-mentioned air intake 12 and exhaust 13, this utility model can ensure the normal entry of external gas and the normal discharge after being compressed twice by the screw compressor 6 and the vane compressor 9.

[0111] Based on the above settings, in a specific embodiment of this utility model, the suction capacity of the screw compressor 6 is 2000m³. 3 / h, the suction capacity of the sliding vane compressor 9 is 500m³ / h. 3 / h.

[0112] This configuration is for a large two-stage compressor. It should be noted that the specific settings for the suction capacity of the screw compressor 6 and the vane compressor 9 are the optimal ratios obtained through multiple tests based on practical experience, in order to meet the requirements of the large two-stage compressor configuration.

[0113] In other words, by configuring the screw compressor 6 and the vane compressor 9 as described above, this utility model can meet the model setting requirements of large two-stage compressors as mentioned above.

[0114] Based on the above settings, in another specific embodiment of this utility model, the suction capacity of the screw compressor 6 is 1000m³. 3 / h, the suction capacity of the sliding vane compressor 9 is 100m³ / h. 3 / h.

[0115] This setting is for small and medium-sized ultra-high compression ratio two-stage compressors. It should be noted that the specific settings of the suction volume of the screw compressor 6 and the suction volume of the vane compressor 9 are the optimal ratios obtained through multiple tests based on practical experience, in order to meet the requirements of the above-mentioned small and medium-sized ultra-high compression ratio two-stage compressors.

[0116] In other words, by configuring the screw compressor 6 and the vane compressor 9 as described above, this utility model can meet the setup requirements of small and medium-sized ultra-high compression ratio two-stage compressors.

[0117] This utility model also proposes an air conditioning system having the above-mentioned two-stage compressor.

[0118] In summary, compared with the prior art, the present invention has at least the following beneficial effects:

[0119] 1. This utility model is a two-stage compressor, which has higher efficiency compared to the traditional compressor structure;

[0120] 2. The high-pressure stage of this utility model adopts a vane compressor, which, compared with the high-pressure stage of a two-stage screw compressor, is designed to handle lower discharge volumes.

[0121] 3. The high-pressure stage of this utility model adopts a vane compressor, which has a smaller size and lower cost compared to the high-pressure stage of a two-stage screw compressor.

[0122] 4. The high-pressure stage of this utility model adopts a vane compressor, which has weaker airflow pulsation compared to the high-pressure stage of a two-stage screw compressor, making the operation of the two-stage compressor more stable.

[0123] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A two-stage compressor, comprising an intake end cap (1), characterized in that, It also includes a screw compressor (6) used as the low-pressure stage of the two-stage compressor, and a vane compressor (9) used as the high-pressure stage of the two-stage compressor; The screw compressor (6) and the vane compressor (9) are connected in series at the rear end of the intake end cover (1).

2. The two-stage compressor according to claim 1, characterized in that, The screw compressor (6) includes a low-pressure stage male rotor (4) and a low-pressure stage female rotor (5), and the low-pressure stage male rotor (4) is connected to a first gear (8); The vane compressor (9) includes a compression shaft (10) connected to a second gear (7); The first gear (8) rotates under the drive of the low-pressure stage male rotor (4), and the first gear (8) is used to drive the second gear (7) to rotate, and the second gear (7) is used to drive the compression shaft (10) to rotate.

3. The two-stage compressor according to claim 2, characterized in that, The first gear (8) is meshed with the second gear (7), and the number of gears in the first gear (8) is less than the number of gears in the second gear (7).

4. The two-stage compressor according to claim 2, characterized in that, The first gear (8) and the second gear (7) are coaxially arranged, and the number of gears in the first gear (8) is greater than the number of gears in the second gear (7).

5. The two-stage compressor according to claim 2, characterized in that, It also includes a motor disposed within the intake end cap (1), the motor having a motor stator (2) and a motor rotor (3); The motor rotor (3) is connected to the low-voltage stage male rotor (4) and drives the low-voltage stage male rotor (4) to rotate.

6. The two-stage compressor according to claim 2, characterized in that, It also includes a plurality of vanes (11) disposed in the vane compressor (9), and the two ends of the vanes (11) abut against the inner wall of the vane compressor (9); When the compression shaft (10) rotates, the plurality of vanes (11) and the inner wall of the vane compressor (9) form a plurality of chambers with periodically changing volumes.

7. The two-stage compressor according to claim 1, characterized in that, It also includes an air intake (12) and an exhaust (13); The air intake (12) is located on the air intake end cover (1), and the exhaust port (13) is located on the housing of the vane compressor (9).

8. The two-stage compressor according to claim 1, characterized in that, The screw compressor (6) has a suction capacity of 2000 m³ / s. 3 / h, the suction capacity of the sliding vane compressor (9) is 500m³ / h. 3 / h.

9. The two-stage compressor according to claim 1, characterized in that, The screw compressor (6) has a suction capacity of 1000 m³ / s. 3 / h, the suction capacity of the sliding vane compressor (9) is 100m³ / h. 3 / h.

10. An air conditioning system, characterized in that, The air conditioning system has a two-stage compressor as described in any one of claims 1 to 9.

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