CN1177062A - turbo compressor - Google Patents

Abstract

The invention discloses a turbine type compressor, which does not require a large moment when starting, can obtain a pushing force suitable for all operating conditions, has high reliability and good compression performance, and has the function of pressing the fixed turbine to the rotating compressor with elastic force. The turbine uses a coil spring that forms a seal between the fixed turbine and the rotating turbine, and moves axially through the compressed gas pressure generated synchronously with the compression operation, and the moving ring that makes the above-mentioned coil spring generate elastic force and pushes the above-mentioned coil spring with a predetermined elastic force. It is a stopper that presses the fixed turbine and prevents the moving ring from continuing to move when the elastic force of the coil spring reaches a predetermined value.

Description

turbo compressor

The present invention relates to a turbo compressor used as a compressor constituting a cooling cycle system in an air conditioner, for example.

For example, in the compressor forming the cooling cycle system of an air conditioner, compared with the ordinary rotary compressor, it is currently tended to use a compressor with extremely low motion noise, good compression performance, and a low number of parts because it does not require components such as suction and discharge valves. Reduced turbo compressor.

The working principle of this kind of compressor is: the vortex-shaped blades of the fixed turbine and the vortex-shaped blades of the rotating turbine are meshed, a compression space is formed between the above-mentioned blades and each turbine mirror plate, and the rotating turbine is rotated. The cooling medium is sucked into the compression space, compressed and then discharged.

However, the sealing of the compression space of the above-mentioned turbo compressor is formed by slidingly fitting the blade ends of the fixed and rotating turbine blades with the opposite end plates respectively.

Thus, if the rotating turbine is forced against the fixed turbine, although the seal can be maintained, the flexible rotation of the rotating turbine is hindered.

Furthermore, compressed spaces are often not necessarily at normal pressure. For example, when a liquid cooling medium is sucked in and compressed, the hydraulic container operating condition occurs, and at this time, the compression space is in an abnormal pressure state. If this state continues for a long time, a large stress will be generated on each turbine blade, and there is a risk of rupture.

Therefore, a method of pressing the above-mentioned fixed turbine to the rotating turbine with a proper pressure to form a compression space seal is proposed here, in an attempt to solve the above-mentioned problems.

For example, in USP3,874,827 (ADL patent), the fixed turbine is pressed to one side of the rotating turbine by the spring pressure together with the compressed high-pressure gas discharge pressure.

In addition, in Japanese Patent Application Publication No. 58-22901 (Toyota Automatic Loom) and Japanese Patent Application Publication No. 7-72541 (Keplande Co-plando), it is proposed that the discharge pressure of the compressed high-pressure gas and the compression process The combination of the intermediate pressure and the combined pressure makes the fixed turbine press to the side of the rotating turbine.

However, in the prior USP invention, there is a problem that the spring presses the stationary turbine to the side of the rotating turbine with the spring force necessary for operation after the stop of operation. In this way, there is a large torque when starting, and a large-capacity motor for driving the compressor must be equipped. As a result, the structure will inevitably be enlarged, and the cost of parts and operating costs will increase.

If the spring with small elastic force is used, the starting torque can be reduced, but the exhaust pressure will also change due to the change of operating conditions, so when the exhaust pressure is high, the pushing force will be too large.

In order to avoid the above problems, the diameter of the exhaust hole can also be reduced. When the exhaust pressure is high, a more suitable pushing force can be obtained, but when the exhaust pressure is very low, there will be Insufficient pushing force and easy separation of the fixed turbine and the rotating turbine damage the seal, resulting in gas leakage and reduced compression performance.

In addition, if the technical solution proposed in JP-A No. 58-222901 or JP-7-72541 uses the discharge pressure and the intermediate pressure to press the fixed turbine to the side of the rotating turbine, the operating conditions of the compressor will The axial force acting on the rotating turbine and the contact force between the fixed turbine and the rotating turbine are too large.

The present invention focuses on solving the above-mentioned problems, and its purpose is to provide a turbo compressor that does not require a large torque when starting, can obtain a suitable pushing force under all operating conditions, and is based on high reliability. On the other hand, compression performance can also be improved.

To achieve the above object, the present invention takes the following technical solutions:

A turbo-type compressor in which a spiral vane 7b of a fixed turbine 7 is engaged with a scroll vane 6b of a rotating turbine 6, and a mirror plate 7a, 6a is formed between each vane 7, 6b and each mirror plate 7a, 6a. Compress the space S, make the rotating turbine 6 rotate, the compressed gas is sucked into the above-mentioned compression space S, the gas is compressed and discharged, and it is characterized in that it has:

The fixed turbine 7 is pressed to the rotating turbine 6 by elastic force to form an elastic member 15 sealed between the two turbines;

The moving part 16 is pushed to move axially by the compressed gas synchronously generated in the compression operation so that the elastic part 15 generates elastic force; and

The elastic component 15 pushes the fixed turbine 7 with a certain elastic force, and when the elastic force of the elastic component 15 reaches a predetermined value, the stop component 17 blocks the movement of the moving component 16 .

Described turbo compressor is characterized in that:

The pressing force that is generated in synchronization with the compression operation and that moves the above-mentioned moving member is the discharge pressure of the compressed high-pressure gas.

Described turbo compressor is characterized in that:

The pushing force that occurs synchronously with the compression operation and moves the above moving parts is generated by the intermediate pressure gas that takes out the gas in the compression process.

Described turbo compressor is characterized in that:

The above elastic member pushes the fixed scroll to the rotating scroll when the compression operation stops.

Described turbo compressor is characterized in that:

There are a plurality of above-mentioned elastic parts, which are arranged at certain intervals relative to the central axis.

A turbo type compressor which has a compressor structure part 4 in which the swirl-shaped blades 7b of the fixed turbine 7 and the swirl-shaped blades 6b of the rotating turbine 6 are engaged with each blade 7b, 6b and each mirror plate A compression space S is formed between 7a and 6a, and the rotary turbine 6 is rotated to suck the compressed gas into the above-mentioned compression space S, compress and discharge the compressed gas, and it is characterized by:

The casing 1 with the above-mentioned compressor structural part 4 inside;

The casing 1 is divided into a separate body 19 on the side of the above-mentioned compressor structure part and the exhaust chamber 23 side of the other part;

Located on the side of the exhaust chamber 23 separated by the above-mentioned separation body 19, and forming the inner cylinder 18 of the discharge pressure chamber 18a that can temporarily receive the high-pressure gas compressed and discharged by the above-mentioned compressor structure part 4;

An outer cylinder 21 arranged at the outer periphery of the inner cylinder 18 at a certain distance from the inner cylinder 18;

The moving part 16 is erected between the inner cylinder 18 and the outer cylinder 21 and is axially moved by the pushing force generated synchronously with the compression operation;

a stop member 17 arranged on the outer cylinder 21 and capable of limiting the movement amount of the moving member 16;

The elastic member 15 is disposed between the separating body 19 and the moving member 16 and elastically presses the fixed turbine 7 to the side of the rotating turbine 6 by the moving force of the moving member 16 .

Described turbo compressor is characterized in that:

The separation body may be any one of the fixed turbine and the back pressure plate provided at a certain distance from the fixed turbine.

Described turbo compressor is characterized in that:

The back pressure plate has the outer cylinder through which the movable member can be inserted from the opposite surface to the fixed turbine, and is provided with an exhaust pressure check valve.

Described turbo compressor is characterized in that:

The above-mentioned moving part is composed of several plate-shaped ring members and a sealing member which is sandwiched between the plate-plate ring members and slides on the peripheral surfaces of the inner cylinder and the outer cylinder and maintains a pressure difference on both sides.

The turbo-type compressor of the said invention is characterized in that the swirl blades of the fixed turbine mesh with the swirl blades of the rotating turbine, a compression space is formed between each blade and each mirror plate, and the The rotary turbine rotates, the compressed gas is sucked into the above-mentioned compression space, and the gas is compressed and then discharged. In the turbo compressor, there is an elastic member that elastically presses the fixed turbine to the rotary turbine to form a seal between the two turbines. The synchronously generated compressed gas pushes the moving part that moves axially to make the elastic part generate elastic force and the elastic part pushes the fixed turbine, and the stop part blocks the moving part from continuing to move when its elastic force reaches a predetermined value.

The above-mentioned invention is characterized in that the pressing force for moving the moving member occurring in synchronization with the above-mentioned compression operation is generated by the discharge pressure of the compressed high-pressure gas.

The said invention is characterized in that the pushing force on the moving member synchronously with the above-mentioned compression operation is generated by the gas having an intermediate pressure during the compression.

The above-mentioned invention is characterized in that the above-mentioned elastic member exerts a pressing force on the stationary turbine to press it toward the rotating turbine even when the compression operation stops.

The above-mentioned invention is characterized in that a plurality of the above-mentioned elastic members are provided at predetermined intervals on the circumference relative to the center.

The turbo compression of the present invention has the following characteristics: in this way, the vortex vanes of the fixed vortex are engaged with the vortex vanes of the rotating vortex, compression spaces are formed between each vane and each end plate, and In the turbo compressor that compresses the compressed gas sucked into it and then discharges the compressor structure part, there is a casing in which the above-mentioned compressor structure part is built, and the casing is divided into the side of the compressor structure part and other parts. The separation body on the side of the exhaust chamber composed of the other parts is formed with an exhaust pressure that is located on the side of the exhaust chamber that is separated and separated and can temporarily receive the high-pressure gas that is compressed and discharged by the above-mentioned compressor structure. The inner cylinder of the chamber, the outer cylinder arranged at a predetermined interval between the inner surface and the outer circumference of the inner cylinder, is erected between the inner cylinder and the outer cylinder, and is axially moved by the pushing force generated synchronously with the compression operation. The moving part is arranged between the separating body and the moving part, and the elastic part is generated by the movement of the moving part to push the fixed turbine and elastically press against the rotating turbine.

The above-mentioned invention has the following features: the above-mentioned separation body may be either the above-mentioned fixed turbine or a back pressure plate provided at a certain distance from the fixed turbine.

The above-mentioned invention has the following features: the above-mentioned back pressure plate not only has the above-mentioned outer cylinder that allows the moving parts to be inserted from the opposite side of the fixed turbine, but also has an exhaust pressure check valve structure.

The above-mentioned invention has the following characteristics: the above-mentioned moving part is composed of several plate-shaped ring members and is sandwiched between the plate-shaped ring members, slides with the outer and inner peripheral surfaces of the outer cylinder at the inner cylinder and is held on both sides. Consists of seals with differential pressure.

According to the above means of solving the problems, a large torque is not required at the time of starting, and the stationary turbine can be pressed against the rotating turbine with an appropriate pressing force under all operating conditions.

Positive effects of the invention:

According to the above invention, since there is an elastic member that presses the fixed turbine to the rotating turbine with elastic force to form a seal between the two turbines, the elastic member is moved axially by the pressure of the compressed gas synchronously generated during the compression operation to make the elastic member move elastically. The elastic force of the component and the elastic component pushes the fixed turbine, and at the same time, when the elastic force reaches a predetermined value, it stops the moving part from moving, so there is no need for a large torque when starting, and a suitable pushing force can be obtained regardless of the operating conditions. , which improves not only reliability but also compression performance.

According to the said invention, since the pressing force for moving the moving parts is generated simultaneously with the compression operation and is generated by the discharge pressure of the compressed high-pressure gas, the structure is simplified and the sealing portion can be minimized.

According to the said invention, since the pushing force to the moving part which occurs synchronously with the compression operation is generated by the gas having an intermediate pressure during the compression, the pushing force to the fixed turbine can be rapidly increased at startup, and the fixed turbine can quickly reach a stable operation state.

According to the above-mentioned invention, since the elastic member presses the fixed turbine to the rotating turbine even when the compression operation is stopped, the loose collision between the fixed turbine and the rotating turbine can be suppressed, and the noise can also be reduced.

According to the above-mentioned invention, since the above-mentioned elastic members are arranged at predetermined intervals on the circumference with respect to the center, the loose impact of the fixed turbine during operation can be suppressed, and the performance can be improved.

According to the invention described above, since there is a separate body separating the compressor structural part from the discharge chamber formed by other components in the casing, the inner cylinder tube which is arranged on one side of the discharge chamber and forms the discharge pressure chamber, is arranged on the A space portion between the outer cylinder and the inner cylinder at a certain distance from the inner cylinder and a moving member moved by an axial thrust force synchronous with the compression operation, provided at the outer cylinder and capable of restricting the movement of the moving member A large number of moving parts and the elastic force generated by the moving and pushing of the moving parts elastically press the fixed turbine to the elastic part on one side of the rotating turbine, so the sealing part is minimized and the structure is simplified, and no large starting torque is required when starting, and A suitable thrust force can be formed under any operating conditions, which not only improves reliability, but also improves compression performance.

According to the above-mentioned invention, the separating body can be any one of the above-mentioned fixed turbine or the back pressure plate provided at a certain distance from the fixed turbine, so the structure is simplified.

According to the above-mentioned invention, the back pressure plate not only has the above-mentioned outer cylinder that allows the moving parts to be inserted from the opposite side of the fixed turbine, but also is provided with the discharge pressure check valve structure, so that the elastic body and the moving body do not occur. In this way, it can not only be assembled correctly and simply, but also improve the assembly manufacturability.

According to the said invention, because the moving part consists of several plate-shaped ring members and is sandwiched between the plate-shaped ring members and is fitted in a sliding manner with the outer and inner peripheral surfaces of the inner cylinder and the outer cylinder and maintains pressure on both sides. Composed of poor seals, it is reliable and simple to maintain the seal.

Embodiments of the present invention are described in detail below with reference to the accompanying drawings:

Fig. 1 is a partial longitudinal sectional view of a turbo compressor according to an embodiment of the present invention.

Fig. 2 is a partial longitudinal sectional view of a turbo compressor according to another embodiment of the present invention.

Fig. 3 is a partial longitudinal sectional view of a turbo compressor according to a third embodiment of the present invention.

Fig. 4 is a schematic longitudinal sectional view of moving parts used in the turbo compressor shown in Fig. 3 .

Fig. 5 is a partial longitudinal section of a turbo compressor and a schematic diagram of a cooling circuit according to a fourth embodiment of the present invention.

Fig. 6 is a schematic diagram showing the comparison of the changing characteristics of the axial pushing force and contact force between the present invention and the traditional structure under different operating conditions.

Figure 1 shows a partial mechanism such as a turbo compressor used in a refrigeration plant.

1 in the figure is an airtight casing, and the airtight casing 1 is provided with a bracket 2 on which a freely rotatable rotary shaft 3 is supported.

The upper part of the above-mentioned rotary shaft 3 and the compressor structural part 4 to be described later are provided with a motor part not shown in the figure at the lower part. The lower end of the rotary shaft 3 is freely rotatably supported in an auxiliary bearing (not shown) protruding from below by the motor part and mounted on the above-mentioned airtight casing 1 .

The above-mentioned compressor structural part 4 is composed of the following components, including a rotating turbine 6 supported in the above-mentioned support 2 by a thrust bearing 5 and freely rotatable, a fixed turbine 7 meshing with the rotating turbine 6 and the fixed turbine 7 Pressing part 8 always presses against rotating turbine 6 .

The rotary turbine 6 is composed of an end plate 6a having a hub 6c fitted with the upper eccentric portion 3a of the rotary shaft 3, and a vortex blade 6b protruding from the top of the end plate 6a and integrated with the end plate.

The fixed turbine 7 is composed of an end plate 7a and a spiral blade 7b protruding from the lower portion of the end plate and integrated with the end plate 7a. The blade 7b is engaged with the blade 6b.

The above-mentioned rotary turbine 6 forms a compression space S between the end plates 6a, 7a of the fixed turbine 7 and the vane plates 6b, 7b, and the volume of the refrigerant gas as compressed gas enters from the peripheral end side and moves toward the center, and its volume gradually changes. Small, play the role of being compressed.

An exhaust chamber 9 communicating with the center of the compression space S is provided on the end plate 6a of the stationary turbine.

The above-mentioned fixed worm gear 7 is supported so as to be movable within a small certain distance in the axial direction. The outer peripheral portion of the end plate 7a of the fixed turbine 7 is formed in a flange shape, and a plurality of outer pin holes 10 are formed through the upper and lower surfaces thereof. Screw holes 11 are provided on the bracket to communicate with the pin holes 10 respectively.

In the pin hole 10 of the end plate 7a of the fixed turbine, slowly insert the casing 12 respectively from above, and its lower end is supported on the support 2 top, wherein the end protrudes slightly from the end plate 7 of the fixed turbine.

A positioning bolt 13 is inserted into the casing 12 , and the lower end of the bolt 13 is screwed into the screw hole of the bracket 2 . A washer 14 is installed between the head of the positioning bolt 3 and the upper end of the sleeve 12 .

Because in the above structure, the casing 12 is fixed between the positioning bolt 13 and the bracket 2 through the gasket 14, and the pin hole 10 of the fixed turbine 7 is slowly inserted into the casing 12, so the fixed turbine 7 can be positioned along the side of the casing 12. Axial movement is free.

However, the range of the above-mentioned movement is only a small distance range between the upper part of the end plate 7a of the fixed turbine and the above-mentioned spacer 14, and this range is determined by the bolt 13 for positioning. That is, the distance between the upper portion of the fixed turbine end plate 7a and the lower portion of the spacer 14 is a gap for determining the movement amount of the fixed turbine 7 .

The pressing part 8 of the above-mentioned fixed worm wheel has an elastic member coil spring 15 that elastically presses the fixed worm wheel 7 to the rotating worm wheel 6 and seals them with each other, and is moved by a force synchronously generated during the compression operation and makes the above-mentioned coil spring 15 elastic. The moving ring 16 and the moving part 17 of force. The moving part 17 is used to prevent the movement of the moving ring 16 when the elastic force of the coil spring 15 reaches a certain value, so that the coil spring 15 pushes the fixed turbine with a predetermined elastic force.

An inner cylinder 18 protruding upward is formed on the upper side of the end plate around the exhaust chamber 9 provided at the central portion of the fixed turbine end plate 7a. The upper portion of the inner cylinder 18 is an open cylinder, which communicates with the exhaust chamber 9, and an exhaust pressure chamber 18a where the high-pressure gas temporarily stays is formed in the cylinder.

An airtight structure with the moving ring 16 is formed on the outer peripheral surface of the inner cylinder 18 and is slidably fitted with each other. One side of the upper part of the moving ring 16 protrudes outwards compared with the lower part, and the cross-section of the joint with the inner cylinder 18 is circular, and most of the rest are flange-like structures with a large diameter.

The above-mentioned coil spring 15 is disposed between the moving ring 16 and the fixed turbine end plate 7a. The inner diameter of the helical spring 15 is slightly larger than the outer diameter of the moving ring 16 and the inner cylinder 18, and one end of the coil spring 15 is in contact with the lower side of the flange-like structure of the moving ring 16 and elastically supports it.

The upper space of the compressor structure 4 in the airtight casing 1 is divided into upper and lower parts by a back pressure plate 19 as a separate body and an exhaust pressure reverse stop valve 20 mounted on the back pressure plate 19 .

The back pressure plate 19 is formed along the upper side of the central axis with a flange joint portion 21 that slides with the outer periphery of the flange-shaped structure of the moving ring 16 and maintains airtightness with each other.

The lower side of the flange joint portion 21 is connected to the above-mentioned stop portion 17 , and the inner side of the stop portion 17 protrudes inward but does not contact the above-mentioned coil spring 15 . When the moving ring 16 moves downward and exceeds the predetermined range, the above-mentioned stop portion 17 can block the legal portion of the moving ring 16, thus limiting its descending height.

There is a gap between the exhaust pressure check valve component 20 and the upper edge of the inner ring 18 , and the upper end opening of the flange joint 21 provided on the back pressure plate 19 is closed as a whole.

A valve seat 22 with a check valve is arranged at its central part, and communicates with the above-mentioned exhaust chamber 9 . That is, the exhaust chamber 9 communicates with the space above the back pressure plate 19 through the valve seat 22 having a check valve.

Like this, by above-mentioned discharge pressure check valve member 20 and back pressure plate 19, the inside of airtight housing 1 is divided into upper and lower two parts, and its upper side space becomes the discharge chamber 23 that the high-pressure gas that discharges temporarily stays.

An exhaust pipe 24 is connected to the upper side of the airtight casing 1, and the exhaust pipe 24 connects the exhaust chamber 23 with the condenser (not shown) of the refrigeration device. A suction pipe not shown in the figure is connected to the lower side of the airtight casing 1, and the suction pipe separates the lower space of the airtight casing 1 separated by the back pressure plate 19 and the discharge pressure check valve part 20 from the refrigeration system. The evaporator of the device is connected (not shown in the figure).

In the turbo compressor with the above structure, when the motor is energized and drives the compressor structural components 4 , the low-pressure refrigerant gas enters the airtight casing 1 through the suction pipe and fills the space under the back pressure plate 19 .

After the refrigerant gas enters the outer peripheral side of the compression space S formed between the rotating turbine 6 and the fixed turbine 7, it is gradually transferred to the center of the inner peripheral side of the compression space S as the rotating turbine 6 rotates, and is compressed due to the smaller volume. compression.

When the predetermined pressure rises, the compressed high-pressure gas is discharged from the discharge chamber 9 and temporarily accumulated in the discharge pressure chamber 18 a, and then enters the discharge chamber 23 through the valve seat 22 of the discharge pressure reverse thrust valve 20 . When the exhaust chamber 23 is full, it is discharged into the external condenser by the exhaust pipe 24 .

As mentioned above, after the compression process starts, after the high-pressure gas discharged from the exhaust chamber 9 fills the discharge pressure chamber 18a, a part of the high-pressure gas will fill the space between the inner ring 18 and the outer cylinder 21. At this time, the high-pressure gas A back pressure is applied to the freely movable moving ring 16 .

The moving ring 16 to which the back pressure is applied moves downward against the elastic force of the coil spring 16, and is stopped by the stop member 17 after descending a predetermined distance, thereby stopping the descending.

On the other hand, due to the decline of the moving ring 16, the coil spring 15 is compressed and deformed. When the moving ring 16 is stopped by the stopper 17 and is in a limited state, the coil spring 15 also acts on the fixed turbine 7 with a predetermined spring force. superior.

Due to the elastic force of the coil spring 15, the fixed turbine 7 is pressed against the rotating turbine 6, ensuring that the compression space S is in a good sealing state during the compression process, thereby improving the efficiency of the compression operation.

In the above structure, the moving ring 16 is pushed and moved by the exhaust pressure generated during the compression operation, so that the coil spring 15 generates elastic force, so the torque required for starting is very small.

During the compression operation, if the pressure in the compression space rises abnormally for some reason, the fixed turbine will float upwards within the contact range with the positioning bolt 14 due to the influence of the abnormal high pressure, thus releasing the sealing state of the compression space S , forming a certain gap.

The abnormally high-pressure gas from the gap can be discharged to the outside of the compression space S, so that abnormal stress will not be generated on the vanes 7b, 6b constituting the fixed and rotating turbines 7, 6, and thus the so-called flexible function is exerted.

On the other hand, as soon as the compression operation is stopped, the pressing force of the moving ring 16 on the coil spring 15 disappears after the exhaust pressure is eliminated. The moving ring 16 floats upward by the elastic restoring force of the coil spring 15 .

After the moving ring 16 comes into contact with the lower side of the discharge pressure check valve member 20, it stops floating upward. In this state, the helical spring 15 acts on the moving ring 16 upwards and the fixed turbine 7 downwards respectively to exert elastic force so that the two parts are close to each other in their respective directions.

That is to say, even when the compressor is stopped, the fixed turbine not only acts on the contact surface of the rotating turbine with its own weight but also with a certain amount of spring force generated by the coil spring 15, so the sealing of the compression space S can still be ensured.

In the above embodiment, the coil spring 15 as the elastic member is wound around the outer periphery of the moving ring 16, but it is not limited to this form actually, and the structure shown in FIG. 2 is also possible.

In FIG. 2, the same reference numerals are assigned to the same components as those already described in FIG. 1, and their descriptions are omitted, and the other components will be described below.

The elastic member 15A constituting the fixed turbine pressing member 8A is formed of a small-diameter coil spring, and several of them are arranged (only one is shown in the figure). Concave mounts 25 are respectively formed on the upper surface of the fixed turbine end plate 7 a and the lower surface of the flange portion of the movable ring 16 , for inserting the upper and lower ends of the coil spring 15A.

In this construction, the operation is exactly the same as that of the previously described compressor except for the fact that there are several coil springs 15A.

In addition, a fixed turbine pressing member 8B as shown in FIG. 3 may also be used.

On the periphery of the fixed turbine end plate 7a and the inner cylinder 18 at a certain distance, an outer cylinder 21a protrudes integrally, and a stop member 17a protruding toward the inner cylinder 18 is fixedly mounted on the upper end thereof.

Between the inner cylinder 18 and the outer cylinder 21a, a movable member 16A (to be described later) is provided with an elastic pressing force applied by an elastic member 15B, and the movable member 16A can freely move up and down.

The above-mentioned elastic members 16b are each formed of a plurality of coil springs, and are provided between the back pressure plate 19a integrated with the discharge pressure check valve member 20 and the above-mentioned moving member 16A.

FIG. 4 is an enlarged schematic view of the above-mentioned moving part 16A. Among them, there is a planar annular seal 30 with an inverted U-shaped section. The upper and lower sides of the seal 30 are respectively pressed with annular plates 31, 32 formed by metal plates. The annular plates 31, 32 are sealed by rivets 32. The plates 30 are riveted together.

As shown in FIG. 3 , the above-mentioned moving member 16A is provided between the inner cylinder 18 and the outer cylinder 21 a. The inner peripheral surface of the sealing member 30 is slidingly engaged with the outer peripheral surface of the inner cylinder 18 , and the outer peripheral surface of the sealing member 30 is fitted with the inner peripheral surface of the outer cylinder 21 a.

On the other hand, between the compression space S formed by the fixed turbine 7 and the rotating turbine 6 and the annular space formed by the inner and outer cylinders 18, 21a and the moving part 16A, there is an intermediate pressure provided on the fixed turbine end plate 7a. The guide hole 33 communicates.

That is to say, before part of the compressed gas in the compression space S rises to a predetermined pressure, it enters the annular space formed by the inner and outer cylinders 18, 21a and the moving part 16A through the intermediate pressure guide hole 33, so the annular space It is also called the intermediate pressure chamber 34 .

When the operation is stopped, due to the elastic force of the coil spring 15B, the moving part 16A is pushed to be in contact with the fixed turbine end plate 7a and tends to be compressed. In this way, the fixed turbine 7 is in contact with the rotating turbine 6, and the sealing of the compression space S is protected.

When the compression operation starts, the gas with intermediate pressure enters the intermediate pressure chamber 34 from the compression space S through the intermediate pressure guide hole 33, and when it is full, it will affect the fixed turbine end plate 7a, part of the surface of the inner and outer cylinders 18, 21a and the moving Part 16A creates a back pressure of intermediate pressure.

At this time, since the moving member 16A moves upward in the drawing, the coil spring 15B is elastically compressed and deformed. Finally, the moving part 16A is stopped by the stop part 7a, so that it cannot continue to move upward.

During the compression operation, since the intermediate pressure chamber 34 is filled with gas having an intermediate pressure, the moving member 16A is always in a state of being stopped by the stopper member 17a. At this time, it corresponds to the state in which the fixed turbine 7 and the moving member 16A are integrated.

Thus, the elastic force of the coil spring 15B is transmitted to the fixed turbine 7 through the moving member 16A, and the fixed turbine 7 is pressed toward the rotating turbine 6 to keep the compression space S sealed.

In this structure, since the volume of the intermediate pressure chamber formed by the intermediate pressure is smaller than the volume of the exhaust pressure chamber formed by the exhaust pressure, the compression stroke and time of the coil spring 15B are shortened when starting, thereby shortening the time from starting. The time required to stabilize the process.

FIG. 5 shows the case where the cooling circuit R is used simultaneously with the release mechanism in the basic structure of the compressor having the fixed turbine pushing member 8A shown in FIG. 2 above.

In this figure, 50 is a condenser, 51 is an expansion device, and 52 is an evaporator. These devices form the cooling circuit R together with the above-mentioned turbo compressor. The above-mentioned release mechanism 40 communicates with the compression space S. As shown in FIG. The gas in the compression process is directly introduced into the cooling circuit R.

For example, supercooling occurs when a cooling room operates during the day and transitions to nighttime. At this time, the on-off valve 41 of the release mechanism 40 is opened to return the gas in the compression process to the cooling circuit R, so that the cooling capacity can be reduced intentionally.

The above-mentioned release mechanism 40 is composed of a release hole 42 basically identical in structure to the above-mentioned fixed turbine 7, which is connected to the end of the release hole 42 and passes through the airtight casing 1 and communicates with the evaporator 52 of the above-mentioned cooling cycle R and the turbine. The release pipe 43 connected to the cold air pipe P between the compressors and the above-mentioned on-off valve 41 arranged in the middle of the release pipe 43 are composed.

A flexible pipe 44 is provided at the position of the release pipe 43 in the airtight casing 1 . The flexible pipe 44 can also be made by forming a helical telescopic pipe from ordinary pipes.

When the rotating turbine 6 rotates, the slight vibration generated by itself will be transmitted to the fixed turbine, and will be further transmitted to the release pipe 43 connected with the fixed turbine, but because the flexible pipe 44 is provided, the above-mentioned vibration can be completely absorbed, preventing the vibration from being released to the outside. pipeline delivery.

That is, due to the flexible tube 44, breakage of the release tube 43 can certainly be prevented.

In an air conditioner with a heat pump cooling cycle, in order to increase the heating capacity of the heating operation, part of the cooling medium discharged from the compressor is bypassed and then input into the compression space, which is an air conditioner with an injection circuit.

In this case, the injection pipe constituting the injection circuit is connected to the end of the injection hole formed in the fixed turbine and communicating with the compression space S. That is to say, in the airtight casing 1, it has the same structure as the compressor described above with FIG.

In Fig. 6, the horizontal axis represents representative air conditioner operating conditions A～F, and the vertical axis represents axial force and contact force, wherein contact force in the present invention refers to the minimum contact force of the fixed turbine and the end of the rotating turbine blade .

Get the minimum value of the contact force of the fixed turbine and the rotating turbine of the present invention to be 1, and then the mutual pushing force (axial force) and the contact force of the turbine in the structure of the present invention obtained by theoretical calculation and the traditional structure are bar graphed, namely and to Figure 5.

In Fig. 6, a represents the pushing force of the structure of the present invention, b represents the pushing force of the conventional structure, c represents the contact force of the structure of the present invention, and d represents the contact force of the conventional structure.

The contact force C of the structure of the present invention is the smallest in the operating condition D, while the contact force d of the conventional structure is the smallest in the operating condition C, and the minimum values thereof are 1, respectively, which are substantially equal.

Compared with the minimum value, the contact force of the structure of the present invention is the largest in operating condition B, about 3.2 times, while the contact force of the conventional structure is the largest in operating condition F, about 4.9 times.

From the analysis of the pushing force, the pushing force a of the structure of the present invention is the largest in the operating condition F, about 9.7 times, while the pushing force d of the traditional structure is the largest in the operating condition E, about 12.2 times.

From the above analysis on the maximum value, it can be known that the compressor in the structure of the present invention can reduce the load compared with the compressor in the traditional structure, thereby improving the reliability and other performances of the compressor.

Claims (9)

1, a kind of turbocompressor, wherein, the swirl shape impeller (7b) of fixed turbine (7) is meshed with the swirl shape impeller (6b) of rotary turbine (6), between each impeller (7,6b) and each runner plate (7a, 6a), is formed with compression volume (S), rotary turbine (6) is rotatablely moved, pressurized gas is inhaled into above-mentioned compression volume (S), with this gas compression and discharge, it is characterized in that having:

With elastic force fixed turbine (7) is pressed to rotary turbine (6) and formed the elastic member (15) that seals between two turbines;

Promote to axially move and make elastic member (15) produce the moving member (16) of elastic force by the pressurized gas of compression synchronous generation in service; With

Described elastic member (15) stops the stop component (17) that moving member (16) moves with certain elastic force pushing fixed turbine (7) when the elastic force of described elastic member (15) reaches institute's definite value.

2, according to right 1 described turbocompressor, it is characterized in that:

Moving the pushing force that produces synchronously and above-mentioned moving member is moved with compression is the exhaust pressure of compressed pressurized gas.

3, turbocompressor according to claim 1 is characterized in that:

Moving the pushing force that takes place synchronously and above-mentioned moving member is moved with compression is to be produced by the intermediate-pressure gas of taking out gas in the compression process.

4, turbocompressor according to claim 1 is characterized in that:

When above-mentioned elastic member stops in the compression operation, fixed turbine is pushed to rotary turbine.

5, turbocompressor according to claim 1 is characterized in that:

Have a plurality of above-mentioned elastic members, its relative central shaft is provided with at regular intervals.

6, a kind of turbocompressor, it has compressor arrangement portion (4), wherein, the swirl shape impeller (7b) of fixed turbine (7) is meshed at each impeller (7b with the swirl shape impeller (6b) of rotary turbine (6), 6b) with each runner plate (7a, be formed with compression volume (S) 6a), rotary turbine (6) rotatablely moved, will be compressed gas suck above-mentioned compression volume (S), with the compression of this pressurized gas and discharge, it is characterized in that having:

In load onto the housing (1) of stating compressor arrangement portion (4);

This housing (1) is divided into above-mentioned compressor structural portion one side and the detached body (19) of exhaust chamber (23)-side of part in addition;

Be located at exhaust chamber (23) one sides that are separated out by above-mentioned detached body (19), and be formed with the inboard cylinder barrel (18) of the exhaust pressure chamber (18a) that can temporarily receive the pressurized gas of discharging by above-mentioned compressor structural portion (4) compression;

Be located at inboard cylinder barrel (18) peripheral part, the outside cylinder barrel (21) that has certain intervals to be provided with inboard cylinder barrel (18);

Be erected at above-mentioned inboard cylinder barrel (18) between the outside cylinder barrel (21) and by moving the axially movable moving member of pushing masterpiece (16) that produces synchronously with compression;

Be arranged on above-mentioned outside cylinder barrel (21) and go up and can limit the stop component (17) of above-mentioned moving member (16) amount of movement;

Be arranged between above-mentioned detached body (19) and the above-mentioned moving member (16), be subjected to the locomotivity of moving member (16), said fixing turbine (7) elasticity is pressed to the elastic member (15) of rotary turbine (6) one sides.

7, turbocompressor according to claim 6 is characterized in that:

Above-mentioned detached body can be that the said fixing turbine reaches either party in the back pressure plate that is provided with at regular intervals with this fixed turbine.

8, turbocompressor according to claim 7 is characterized in that:

Above-mentioned back pressure plate has can make the above-mentioned outside cylinder barrel of above-mentioned moving member from the opposing side insertion of an opposite side with fixed turbine, and is provided with exhaust pressure safety check portion.

9, turbocompressor according to claim 1 is characterized in that:

Above-mentioned moving member is by several tabular ring elements and be clipped between this plate plate ring element that side face with inboard cylinder barrel and outside cylinder barrel slips and the Sealing that maintains pressure difference in both sides is formed.

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