JP3728514B2 - Gas compressor - Google Patents

Description

[0001]
[Industrial application fields]
The present invention relates to a gas compressor that can also be used as an expander. In particular, the present invention does not require an intake valve and a discharge valve, and is intended to obtain a highly efficient trochoid gas compressor having a very small vibration and a simple structure. Is.
[0002]
[Prior art]
An example of a compressor without a suction valve and a discharge valve is a screw type gas compressor, but the tooth shape is three-dimensional and requires advanced processing technology. May be disadvantageous.
There are also rotary compressors of variable blade type or scroll type structure, but even if this is called a rotary type, it basically has a crankshaft and is non-equilibrium structure, so it is easy to generate vibration and high speed. It is not intended for rotation.
[0003]
Conventionally, a Wankel type engine having the smallest number of teeth is well known as a trochoid type fluid machine, but basically it has a crankshaft and has a non-equilibrium structure.
As a trochoid type fluid machine, an outer rotor having a trochoid curve on its inner peripheral surface is driven and rotated by an inner rotor inscribed therewith, which is exactly the same as a liquid pump using a circumscribed or inscribed gear. It has been handled and used as a liquid pump to date.
[0004]
[Problems to be solved by the invention]
However, here it is necessary to compare the conventional gear pump with the rotary trochoid pump. In the former, liquid is sucked from the suction port, and the volume of the sucked liquid reaches the discharge port without changing as it is, and is discharged and pumped.
In the latter case, when gas is sucked from the suction port, the space of the sucked liquid is sealed, and the volume of the space gradually reaches the dead center of compression end while being gradually reduced with the rotation angle. An outlet is provided and discharged from this.
[0005]
Since the liquid is incompressible, the latter trochoid pump is currently used as a liquid pump, and the suction port and the discharge port must be adjacent to each other so that compression is not performed. It can be seen that the latter trochoid pump basically has a function as a gas compressor rather than an essential function as a liquid pump.
Therefore, the trochoid pump inscribed around the circumference which has been used as a liquid pump exhibits its function most when applied as a gas compressor or a gas expander as it is.
[0006]
However, all-round inscribed trochoidal tooth type pumps that have been used for hydraulic pressure feeding up to now, the meshing part between the inner rotor and outer rotor, the sliding part with the side cover, etc., will leak in the case of gas compression. Since it becomes a place where it occurs, high-level processing is required, and as a result, its practical use has been difficult.
[0007]
In order to achieve this technical problem, an object of the present invention is to provide a highly efficient gas compressor without causing leakage even when a trochoid gas compressor is configured.
Another object of the present invention is to provide a highly efficient gas compressor having a simple structure and very little vibration.
[0008]
[Means for Solving the Problems]
In order to achieve this technical problem, the present invention provides a side cover 41, 42 provided with at least one of the discharge port 6 and the suction port 8 as shown in FIG. An inner rotor 1 that is pivotally supported and has a trochoidal tooth shape on the outer peripheral surface, an outer rotor 2 that has an inner envelope side inscribed in correspondence with the outer periphery of the inner rotor 1, and an inner rotor 1 axial center An outer rotor housing 3 fitted to the outer peripheral side of the outer rotor 2 for rotating the outer rotor 2 eccentrically, and a liquid inlet 10 facing the inter-rotor compression space A between the inlet 8 and the outlet 6 are provided. Prepared,
The first feature is that gas compression is performed while the compression space A is sealed with the liquid.
The second feature is that the liquid inlet 10 is connected to a discharge side tank of the compressor or a liquid receiving tank communicating with the compressor, and liquid can be supplied to the liquid inlet 10 from a liquid portion of these tanks. By doing so, the injection liquid for sealing the sliding portion is in the circulation system, and the specially-designed liquid pump complicates the structure of the system and is designed to be avoided.
Such a configuration is extremely effective as a compressor for a refrigerator incorporated in a refrigeration cycle.
[0009]
The rotor may be driven such that the inner rotor 1 is pivotally supported on the side covers 41 and 42 via a drive shaft, and the outer rotor 2 can be rotated by the drive rotation of the inner rotor 1. The inner rotor 1 may be configured to be rotatable by driving and rotating the outer rotor 2 or the rotor housing 3 and following the driving rotation.
The present invention can be used as a gas expander by switching the discharge port 6 and the suction port 8 as a gas compressor in reverse.
[0010]
[Action]
According to such technical means, an appropriate amount of liquid is injected into the compression space A at a portion having an appropriate compression angle from the liquid injection port 10 facing the inter-rotor compression space A between the suction port 8 and the discharge port 6. The leakage of gas in the compression space A can be effectively prevented.
Further, interposing the outer rotor housing 3 on the outer peripheral side of the outer rotor 2 makes it possible to reduce the rotational speed and to make the high speed rotation effective in preventing gas leakage. In this case, between the outer rotor 2 and the housing 3 More preferably, a bearing 17 or a low friction member is interposed.
[0011]
Next, when the discharge port 6 and the suction port 8 are provided on the side cover 41 or 42 side, the fluid makes a U-turn in the process of suction and discharge. The flow is not smooth.
In this case, it is preferable that the suction port 8 is arranged in one side cover 41 and the discharge port 6 is arranged in the other side cover 42 so that the flow in the machine can be unidirectional.
[0012]
Next, the gas from the suction port 8 is confined in the space until it comes into contact with the discharge port 6 from the suction port 8, and is reduced and compressed according to the rotation angle, but is discharged with the compression pressure in the machine and the discharge port 6 as a boundary. If the discharge port 6 is opened at a point where the external pressure becomes equal, the compressed gas does not enter and exit from the discharge port 6. In other words, there is no occurrence of repeated loss of expansion and compression, and compression is performed. An effect can also be given. The position of the discharge port 6 with respect to the compression end dead center Y1 and the shape of the discharge port 6 are important.
Therefore, the line connecting the compression end dead center Y1 and the inner rotor 1 axial center by the inner rotor 1 and the outer rotor 2 is a boundary, and the discharge port 6 is disposed on the upstream side in the rotor rotational direction from the boundary position of the dead point Y1 and on the downstream side. A suction port 8 is preferably provided.
[0013]
Further, the outer rotor housing 3 is configured to be displaceable by a predetermined angle in the compressor frame with the axis of the inner rotor 1 as the center, and by the displacement, the discharge port 6 is opened with the discharge port 6 as a boundary and the external pressure inside and outside the device is an equal pressure point. It is good to let them.
Furthermore, the pressure generated when the gas is compressed is related to the suction pressure, the rotational speed, the type of gas, the amount of liquid injected for sealing, and the position of the discharge port 6 must correspond to these. It will be. It is also desirable to automatically handle this in order for both to be always performed with the equal pressure.
Therefore, the rotor housing 3 is preferably displaced by a predetermined angle using the pressure difference between the inside and outside of the machine with the discharge port 6 as a boundary, and the gas compression volume ratio at the discharge port 6 is automatically controlled and operated.
[0015]
Further, this can be used as an expander in which the suction port 8 and the discharge port 6 are reversed. In this case, the shaft output of the inner rotor can be used as a power source.
Furthermore, it is possible to use a plate having a discharge port 6 for a low compression ratio and a discharge port 6 for a high compression ratio by configuring the discharge port 6 with a port plate body and making the plate body replaceable. .
Furthermore, the drive shaft of the inner rotor 1 can be used in a hermetic compressor for air conditioning by adopting a cantilever shaft cantilever structure.
[0016]
【Example】
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described in this embodiment are not intended to limit the scope of the present invention only to specific examples unless otherwise specified. Not too much.
1A and 1B are explanatory views of the present invention, in which FIG. 1A is a cross-sectional view of the Y-Y axis surface of FIG.
Reference numeral 1 denotes an inner rotor having a trochoidal tooth shape on the outer peripheral side, a pair of side covers 41 fitted with a rotation shaft on the axis of the intersection of the Y-Y axis and the XX axis and arranged facing each other on both sides, 42 is rotatably supported.
The rotating shaft protrudes from the other side covers 41 and 42 and can be directly connected to a motor (not shown).
[0017]
The trochoid outer rotor 2 has a cylindrical shape, has an inscribed envelope corresponding to the inner rotor 1 on the inner peripheral surface side thereof, and functions as an idler that rotates following the inner rotor 1.
The trochoid outer rotor 2 is housed rotatably in a rotor housing 3 housed in a circular compressor case.
The cylindrical rotor housing 3 is formed by decentering the inner rotor housing space by (x−X) with respect to the axis of the inner rotor 1, so that the outer rotor 2 is (x−X) with respect to the inner rotor 1. ) Since the rotation is eccentric, the YY axis connecting the compression end dead center Y1 and the inner rotor 1 axial center by the inner rotor 1 and the outer rotor 2 is a boundary, and the rotor rotational direction downstream from the boundary position of the dead point Y1. On the side, the space volume between the rotors expands in the direction of gradually expanding, and the space volume between the rotors is reduced in the direction of gradually compressing from the compression start point on the opposite side of 180 °.
Therefore, one side cover 41 has an arcuate slanted inlet 8 and a suction pipe 9 communicating with the other side cover 42 at a position facing the expansion space B on the right side of the Y-Y axis. A discharge port 6 that is a fraction of the size of the suction port 8 and a discharge pipe 7 that communicates with the discharge port 6 are provided in an arc shape at a position facing the compression space A on the left side of the Y-Y axis.
[0018]
The gas from the suction port 8 is compressed in the meshing space of the inner rotor 1 and the outer rotor 23, and the gas flow in the machine to the discharge port 6 can be unidirectional.
Further, the other side cover 42 has a rotational advance angle position with respect to the discharge port 6, in other words, a position facing the compression space A between the rotor 8 between the suction port 8 and the discharge port 6. A liquid injection port 10 for sealing is provided, and a required amount of liquid is injected into the machine.
[0019]
As shown in FIG. 5, the side cover 42 is configured such that the discharge port 6 portion can be separated and replaced as a plate body 421, and both are configured to be hermetically positioned and joined by a positioning pin 422 and an O-ring 423. You can also
As a result, it is possible to prepare the plate bodies 421 having the discharge ports 6 for the low compression ratio and the discharge ports 6 for the high compression ratio, and replace them as necessary.
[0020]
The outer peripheral axis of the rotor housing 3 that encloses the outer rotor 2 is aligned with the axial center of the inner rotor 1, so that it is rotated inside the compressor frame 4 by a predetermined angle about the same axis as the inner rotor 1. Can be displaced.
As a result, by rotating the rotor housing 3 at an appropriate angle, the discharge port is located at a position where the compression pressure in the discharge pipe 7 and the compression pressure to the inflowing gas due to the meshing of the inner rotor 1 and the outer rotor 2 become equal. 6 can be adjusted to open.
[0021]
That is, the rotation of the rotor housing 3 causes the relative position of the compression end dead center Y1 to rotate relative to the fixed position of the discharge port 6, which results in the rotation of the position where the trochoidal teeth mesh. Because.
The adjustment of the rotation may be performed manually. For example, as shown in FIG. 2, a tooth surface 31 is formed on a part of the side surface of the housing 3, and a screw shaft 161 that meshes with the tooth surface 31 is used as an actuator. 16 is connected to an output shaft of 16, the differential pressure between the pressure sensor 13 in the discharge port 6 and the pressure sensor 14 in the discharge pipe 7 is compared by the comparison detector 15, and the actuator 16 is rotated by a predetermined amount by the output, The rotor housing 3 is automatically displaced by a predetermined angle, whereby the outer rotor 2 housed in the housing 3 is also displaced, and the distance between the discharge port 6 position and the compression end dead center Y1 position can be relatively adjusted.
[0022]
Next, in order to rotatably configure the outer rotor 2 serving as an idler and the rotor housing 3, the outer rotor 2 can be rotated lightly by interposing it with a low sliding resistance member such as a fluororesin or a ball or a roller bearing 17. It is better to allow rotation.
Unlike the present embodiment, by configuring the outer rotor 2 as a driving side and the inner rotor 1 to be driven to rotate, a further high speed operation is possible, but the structure is somewhat complicated.
[0023]
In addition, liquid injection from the liquid injection port 10 for sealing the sliding portion may be performed by a special injection pump, but as shown in FIG. 2 and FIG. 4, the liquid storage part 121 of the discharge tank 12 or By supplying liquid from a liquid receiving tank (not shown) communicating with this, it is not necessary to provide the infusion pump.
It is needless to say that the configuration as described above can be used as a refrigeration compressor that compresses refrigerant gas without any particular restriction on gas compression.
Further, the discharge side can be used as a gas expander with the suction side as the suction side and the suction side as the discharge side, and this switching can also be performed by rotating the rotor housing 3. The shaft output can be used as a power source.
[0024]
【The invention's effect】
As described above, according to the present invention, the inscribed trochoid pump that has been used only for hydraulic feeding can satisfy the function as a gas compressor.
Furthermore, the present invention has a structure suitable for a gas compressor because it can withstand high-speed rotation because it is a symmetric static or dynamic equilibrium type without using a crankshaft. In addition, a highly efficient gas compressor can be easily operated in a small, light, and quiet manner.
It has various effects such as.
[Brief description of the drawings]
BRIEF DESCRIPTION OF DRAWINGS FIG. 1 is a trochoid compressor according to an embodiment of the present invention, in which (A) is a cross-sectional view of the Y-Y axis surface of (B), and (B) is a partial cross-sectional view of the side surface.
FIG. 2 is an overall schematic diagram showing the compression volume control system of FIG. 1;
3 shows a modification of FIG. 1 in which a bearing is interposed between the outer rotor and the housing.
4 is an overall schematic diagram showing the infusion solution control system of FIG. 1. FIG.
FIG. 5 shows a modification of FIG. 1 in which the discharge port has a replaceable plate structure.
[Explanation of symbols]
6 Discharge port 8 Suction port 41, 42 Side cover 1 Inner rotor 2 Outer rotor 3 Outer rotor housing 10 Liquid injection port A Compression space

Claims (10)

A side cover provided with at least one of a discharge port and a suction port;
An inner rotor pivotally supported between the pair of side covers and having a trochoidal tooth shape on the outer peripheral surface;
An outer rotor provided on the inner peripheral side with an envelope inscribed in correspondence with the outer periphery of the inner rotor;
An outer rotor housing fitted to the outer peripheral side of the outer rotor in order to rotate the outer rotor eccentric with respect to the inner rotor axis;
A liquid injection port facing the compression space between the rotor between the suction port and the discharge port;
While letting gas compression while sealing the compression space with the liquid ,
The gas compression is characterized in that the liquid inlet is connected to a discharge side tank of the compressor or a liquid receiving tank communicating with the compressor, and liquid can be supplied to the liquid inlet from a liquid part of these tanks. Machine.   A line connecting the compression end dead center and the inner rotor axial center by the inner rotor and the outer rotor is used as a boundary, and a discharge port is provided on the upstream side in the rotor rotation direction from the boundary position of the dead point, and a suction port is provided on the downstream side. The gas compressor according to claim 1.   3. The gas compressor according to claim 2, wherein the suction port is allocated to one side cover and the discharge port is allocated to the other side cover.   The outer rotor housing is configured to be displaceable by a predetermined angle within the compressor frame around the axis of the inner rotor, and the displacement opens the discharge port at an equal pressure point with the discharge port as a boundary. The gas compressor according to claim 1, wherein   2. The gas compression volume ratio at the discharge port is automatically controlled and operated by displacing the rotor housing by a predetermined angle using a differential pressure inside and outside the machine with the discharge port as a boundary. Gas compressor.   2. The gas compressor according to claim 1, wherein a bearing or a low friction member is interposed between the outer rotor and the rotor housing.   The gas compressor according to claim 1, wherein the inner rotor is pivotally supported on a side cover via a drive shaft, and the outer rotor can be rotated by being driven by rotation of the inner rotor.   The gas compressor according to claim 1, wherein the outer rotor or the rotor housing side is driven to rotate, and the inner rotor can be rotated by being driven by the driving rotation.   The gas compressor according to claim 1, wherein the gas compressor is used as a gas expander by switching a discharge port and a suction port as a gas compressor in reverse.   2. The gas compressor according to claim 1, wherein the discharge port is constituted by a port plate body, and the plate body is exchangeable.

Images