JP2857234B2 - Scroll type fluid machine - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll type fluid machine suitable for use in, for example, a compressor or a vacuum pump, and in particular, lubricating oil or the like between a orbiting scroll and a fixed scroll. The present invention relates to an oilless scroll type fluid machine that does not supply oil.

[Prior Art] FIG. 3 shows an example in which a scroll type fluid machine of the prior art is used as a horizontal type air compressor.

In the figure, reference numeral 1 denotes a casing, 2 denotes a bottomed cylindrical casing main body which constitutes the casing 1 together with a front casing 3 described later, and the casing main body 2 has a disc-shaped bottom 2A and a bottom 2A. A bearing portion 2B extending into the casing main body 2 from the peripheral side, and a front casing 3 from the outer peripheral side of the bottom portion 2A.
And a cylindrical portion 2C extending in the direction of.

Reference numeral 3 denotes a front casing which is integrally provided at the distal end side of the cylindrical portion 2C of the casing main body 2 and is formed in a short stepped cylindrical shape. An annular portion 3A is integrally formed to protrude, and a thrust receiving portion 3B is formed on the inner peripheral side of the annular portion 3A so as to slidably contact the outer peripheral side of the back surface 7B of the orbiting scroll 6 described later and receive a load in the thrust direction. ing. The thrust receiving portion 3B is provided with a rotation preventing mechanism (not shown) between the thrust receiving portion 3B and the orbiting scroll 6.

Reference numeral 4 denotes a drive shaft rotatably supported on bearings 2B of the casing body 2 around bearings 5, 5 around an axis OO. The distal end side of the drive shaft 4 extends into the casing 1 and extends. next crankshaft 4A, the axis O ₁ -O ₁ of the crankshaft 4A is adapted to eccentrically by a predetermined distance d with respect to the axis O-O of the drive shaft 4. The base end of the drive shaft 4 is connected to a motor (not shown) outside the casing 1 and is driven to rotate by the motor.

Reference numeral 6 denotes an orbiting scroll which is located between a thrust receiving portion 3B of the front casing 3 and a thrust receiving portion 15 of a fixed scroll 11 which will be described later, and is rotatably mounted on the crankshaft 4A. End plate 7 formed in a shape
And a spiral wrap portion 8 erected on the front surface 7A side of the end plate 7 with the center side as the winding start end and the outer periphery side as the end end, and a boss provided at the center of the back surface 7B side of the end plate 7 The boss 9 has a crankshaft 4 </ b> A mounted via a swing bearing 10. And the orbiting scroll 6
When the drive shaft 4 is driven to rotate, a circular motion having a turning radius of dimension d is given by the crankshaft 4A,
The rotation preventing mechanism prevents the rotation movement, and keeps turning (orbiting) around the axis OO of the drive shaft 4.

Reference numeral 11 denotes a fixed scroll which is fixed to the front surface of the front casing 3 by abutment so as to cover the front end side of the casing 1. The fixed scroll 11 has its center aligned with the axis OO of the drive shaft 4. End plate arranged on the center side to match
12, a spiral-shaped wrap portion 13 erected on the inner surface side of the end plate 12, and a cylindrical support portion 14 formed on the outer peripheral side of the end plate 12 and having a U-shaped cross section. The support portion 14
An annular plate 15 which abuts with the front casing 3 is integrally formed at the distal end of the casing. The inner peripheral side of the annular plate 15 is in sliding contact with the end plate 7 of the orbiting scroll 6,
An annular thrust receiving portion 15A that receives a load in the thrust direction from the orbiting scroll 6 is formed to face the thrust receiving portion 3B of the front casing 3.

Here, the wrap portion 13 of the fixed scroll 11 is disposed so as to overlap with the wrap portion 8 of the orbiting scroll 6 by being shifted by a predetermined angle. Compression chambers 16, 16,... As a plurality of hermetically closed spaces are defined.

Reference numerals 17 and 18 denote a suction port and a discharge port formed in the fixed scroll 11, and the suction port 17 is formed on the outer peripheral side of the supporting portion 14 so as to communicate with the compression chamber 16 on the outermost peripheral side. Is formed at the center of the end plate 12 so as to communicate with the compression chamber 16 on the most central side. Reference numeral 19 denotes a counterweight provided on the drive shaft 4 in the casing 1, and the counterweight 19 is configured to balance the rotation of the drive shaft 4 and the orbiting scroll 6.

20 is an air tank for storing compressed air.
Reference numeral 20 is connected to a discharge port 18 of the fixed scroll 11 via a discharge pipe 21. Reference numeral 22 denotes a manual valve provided on the discharge side of the air tank 20, and the amount of compressed air supplied from the air tank to an external pneumatic device can be adjusted by adjusting the valve opening of the valve 22. It has become.

The scroll-type fluid machine according to the prior art has the above-described configuration. When the drive shaft 4 is driven to rotate by a motor, the rotation is transmitted from the crankshaft 4A to the orbiting scroll 6 via the orbiting bearing 10, and the orbiting scroll 6 Are turned around the axis OO of the drive shaft 4 with a turning radius of the dimension d, and are defined between the wrap portion 8 of the orbiting scroll 6 and the wrap portion 13 of the fixed scroll 11. By continuously reducing the compression chamber 16 and compressing the air sucked from the suction port 17 in each compression chamber 16, the compressed air is discharged from the discharge port 18 to the air tank 20 via the discharge pipe 21 sequentially. With this, a compression action is performed. The compressed air stored in the air tank 20 is supplied to the valve 22
And supplied to an external pneumatic device or the like.

[Problems to be solved by the invention]

However, in the above-described conventional technique, compression heat is generated in each compression chamber 16 during the compression action, and friction heat due to rotation is generated between the orbiting scroll 6, the orbiting bearing 10, the thrust receiving portion 15A of the fixed scroll 11, and the like. Is generated, the heat is transmitted to the orbiting scroll 6 and the fixed scroll 11, and the temperatures of the wrap portions 8 and 13 of the orbiting scroll 6 and the fixed scroll 11 increase. In particular, in a non-lubricated scroll type air compressor, these temperature rises are remarkable as compared with a lubricated type air compressor, so that each wrap portion 8, 13 thermally expands according to this temperature rise, and each wrap portion 8, 13 The clearance δ in the thrust direction between the tip and the roots of the end plates 7 and 12 is reduced, and the tip surfaces of the wrap portions 8 and 13 come into contact with the end plates 7 and 12, respectively, resulting in the "spotting" phenomenon. Tends to occur.

For this reason, in the prior art, the height dimension of each of the wrap portions 8 and 13 is shortened in advance and the thrust direction clearance δ is increased by an amount corresponding to a dimension that thermally expands according to a temperature rise in the operating state of the compressor. However, it takes time for the wrap portions 8, 13 to rise in temperature due to the compression action and thermally expand, and it takes time for the clearance δ in the thrust direction to reach an optimal predetermined size, so that the starting performance of the compressor is reduced and the compression efficiency is reduced. There is a problem of lowering. In particular, when starting and operating the compressor with the valve 22 largely opened, the air tank 20,
Since it takes time for the pressure inside the discharge pipe 21 to rise to the predetermined pressure, there is a problem that the efficiency of the compression action is reduced and the start-up performance of the compressor is greatly reduced.

The present invention has been made in view of the above-described problems of the related art, and the present invention can quickly set the thrust direction clearance between each lap portion and each end plate to a predetermined size after starting the compressor, An object of the present invention is to provide a scroll-type fluid machine capable of greatly improving the start-up performance of a compressor.

[Means for solving the problem]

The feature of the configuration adopted by the present invention to solve the above-mentioned problem is that the solenoid valve provided on the discharge port side of the fixed scroll and the thrust direction clearance between the orbiting scroll and the fixed scroll after starting have a predetermined dimension. And a solenoid valve control means for controlling the solenoid valve to be in a closed state until reaching.

Further, it is preferable that the solenoid valve control means is constituted by a time controller for setting a predetermined time after activation.

Further, the electromagnetic valve control unit may be configured to control the electromagnetic valve to be in a closed state based on a detection signal from a temperature detection unit that detects a temperature of the orbiting scroll or the fixed scroll.

[Action]

With the above configuration, the solenoid valve is closed by the solenoid valve control means at the time of startup, and the fluid sucked from the suction port can be repeatedly compressed in the closed space. Then, as the pressure in the closed space increases, each wrap portion of the orbiting scroll or the fixed scroll increases in temperature and thermally expands, and the thrust direction clearance between the orbiting scroll and the fixed scroll is quickly adjusted to a predetermined size. When this thrust clearance reaches a predetermined dimension,
The solenoid valve control means can perform normal operation by opening the solenoid valve.

Further, when the solenoid valve control means is constituted by a time controller, if the time required for the clearance in the thrust direction between the orbiting scroll and the fixed scroll to reach a predetermined dimension by the compression action after activation is set in advance, the predetermined time can be obtained. The solenoid valve can be automatically opened after a lapse of time.

Further, the temperature detection means can detect the temperature of the orbiting scroll or the fixed scroll, and the electromagnetic valve control means, based on the detection signal, operates until the clearance in the thrust direction between the orbiting scroll and the fixed scroll reaches a predetermined dimension. The valve can be closed.

〔Example〕

Hereinafter, an embodiment of the present invention will be described with reference to FIGS. 1 and 2 by taking as an example a case where it is used as a horizontal type air compressor. In the embodiments, the same components as those of the above-described related art are denoted by the same reference numerals, and description thereof will be omitted.

FIG. 1 shows a first embodiment of the present invention.

In the figure, reference numeral 31 denotes a discharge pipe, which is provided between the discharge port 18 and the air tank 20 in substantially the same manner as the discharge pipe 21 described in the related art. tube
An electromagnetic valve 32 described later is provided in the middle of 31.

Reference numeral 32 denotes a normally-open type solenoid valve which is provided on the discharge port 18 side and is provided in the middle of the discharge pipe 31 and is closed by energization from the outside. It is connected to the controller 34. The electromagnetic valve 32 closes when power is supplied from the time controller 34 via the lead wire 33, and shuts off the space between the discharge port 18 and the air tank 20.

34 is a time controller as a solenoid valve control means,
In the time controller 34, a predetermined time from the start until the thrust direction clearance δ reaches a predetermined dimension is set in advance in each of the wrap portions 8, 13 due to the compression action. And the time controller
34, after the compressor is started, the solenoid valve 32 is energized via the lead wire 33 until the set predetermined time elapses, and the solenoid valve
The valve 32 is closed to increase the pressure in each compression chamber 16, thereby thermally expanding each of the wrap portions 8 and 13 to make the thrust clearance δ a predetermined size, and after a predetermined time has elapsed, the electromagnetic valve The power supply to the compressor 32 is stopped and the valve is opened to allow normal operation of the compressor.

The scroll-type air compressor according to the present embodiment has the above-described configuration, and there is no particular difference in the basic operation.

However, in this embodiment, the discharge pipe is located on the discharge port 18 side.
Since an electromagnetic valve 32 provided in the middle of 31 and a time controller 34 for energizing the electromagnetic valve 32 and closing the valve until a predetermined time elapses after activation are provided, for example, the valve of the air tank 20 is provided. Even when the valve 22 is largely opened, the solenoid valve 32 is closed until a predetermined time has elapsed from the start of the compressor, the inside of the discharge pipe 31 is shut off, and air sucked from the suction port 17 is allowed to flow into each compression chamber 16. Can be repeatedly compressed, thereby effectively increasing the pressure in each compression chamber 16, each wrap portion 8, 13 is quickly thermally expanded by the compression heat at this time,
Various effects can be achieved, for example, the clearance in the thrust direction δ can be quickly set to a predetermined size, and the rising performance of the air compressor can be greatly improved.

FIG. 2 shows a second embodiment of the present invention. The feature of this embodiment is that the solenoid valve is controlled to be in a closed state based on a detection signal of a temperature sensor provided on the end plate of the fixed scroll. I did it.

In the figure, reference numeral 41 denotes a temperature sensor as temperature detecting means provided on the end plate 12 of the fixed scroll 11, and the temperature sensor 41 is made of a temperature-sensitive material such as a thermistor. And
The temperature sensor 41 detects the temperature of each of the wrap portions 8, 13 and the end plate 12, and outputs a detection signal to a temperature controller 43 described later via a lead wire.

Reference numeral 43 denotes a temperature controller as electromagnetic valve control means, and the temperature controller 43 controls the electromagnetic valve 32 when the temperature of each of the wrap portions 8, 13 and the like detected by the temperature sensor 41 at startup is lower than a predetermined temperature.
And the solenoid valve 32 is closed to shut off the suction pipe 31, thereby increasing the pressure in each compression chamber 16 to thermally expand each of the wrap portions 8, 13, When the temperature of each of the wrap portions 8 and 13 rises and the temperature in the thrust direction clearance δ reaches a predetermined size, the power supply to the solenoid valve 32 is stopped and the communication between the discharge port 18 and the air tank 20 is established. Let
Normal driving is allowed.

Thus, in the present embodiment configured as described above, substantially the same operation and effect as in the first embodiment can be obtained. In particular, in the present embodiment, each of the wrap portions 8 and The temperature controller 43 is configured to control the solenoid valve 32 to the closed state based on the temperature of the thirteen. Therefore, even when there is a temperature change in summer, winter or the like, or in the case of restarting immediately after operation stop, etc. Thus, the start-up performance of the air compressor can be reliably improved.

In each of the above embodiments, the normally-open solenoid valve 32 that is closed by external energization has been described. However, a normally-open solenoid valve that is opened by external energization is used instead. In this case, after the operation is stopped, the compressed air from the air tank 20 flows backward through the discharge pipe 31 toward the discharge port 18, thereby preventing the orbiting scroll 6 from rotating in the reverse direction. Above, for example, a three-phase motor is used to rotationally drive the drive shaft 4, and even if the connection of this motor is mistaken and the orbiting scroll 6 rotates in the reverse direction, air cannot be sucked from the discharge port 18 because each compression chamber The compression action at 16 can be prevented, and the fail-safe function of the air compressor can be greatly improved.

In the second embodiment, the temperature sensor 41 as the temperature detecting means is constituted by a thermistor,
Although described as being provided on the end plate 12 of the present invention, the present invention is not limited to this. For example, a temperature relay made of bimetal or the like may be used as the temperature detecting means, and this may be provided on the end plate 7 of the orbiting scroll 6 or the like. In this case, since the temperature relay can also serve as the solenoid valve control means, the temperature controller 43 can be eliminated and the configuration can be simplified.

Further, in each of the above embodiments, the case where the scroll fluid machine is used as an air compressor has been described as an example.
The present invention is not limited to this, and may be used as, for example, a vacuum pump connected to a vacuum container or the like to generate a vacuum.

Further, in each of the embodiments described above, an oilless scroll type fluid machine has been described as an example. However, the present invention is not limited to this, and can be applied to an oil type scroll type fluid machine. Further, the fixed scroll 11 and the annular plate 15 may be formed separately and fixed with bolts or the like.

〔The invention's effect〕

As described above in detail, according to the present invention, the solenoid valve provided on the discharge port side of the fixed scroll and the solenoid valve are closed until the thrust direction clearance between the orbiting scroll and the fixed scroll reaches a predetermined size after startup. Since the solenoid valve control means for controlling the valve state is provided, the solenoid valve can be closed at the time of startup by the solenoid valve control means, and the fluid sucked from the suction port can be repeatedly compressed in the closed space, and this pressure increase The wrap portion of the orbiting scroll or the fixed scroll is quickly thermally expanded by the compression heat generated by the
The clearance in the thrust direction between the orbiting scroll and the fixed scroll can be set to a predetermined size, and the rising performance of the scroll air compressor can be greatly improved.

Further, if the solenoid valve control means is constituted by a time controller, a time period in which the thrust clearance between the orbiting scroll and the fixed scroll in the thrust direction reaches a predetermined dimension by the compression action after activation is set in advance. After the lapse of time, the solenoid valve can be automatically opened.

Furthermore, if the solenoid valve control means controls the solenoid valve to be in the closed state based on the detection signal of the temperature detection means,
Even in the case of a temperature difference in winter or the like, or in the case of restarting immediately after stopping the operation, the clearance in the thrust direction can be quickly set to a predetermined size without waste.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a scroll type air compressor showing a first embodiment of the present invention, FIG. 2 is a longitudinal sectional view of a scroll type air compressor showing a second embodiment of the present invention, and FIG. FIG. 1 is a longitudinal sectional view of a scroll compressor showing a conventional technique. 1 ... casing, 4 ... drive shaft, 4A ... crank shaft,
6 orbiting scroll, 7,12 head plate, 8,13 wrap portion, 10 orbiting bearing, 11 fixed scroll, 16 compression chamber (closed space), 17 suction port, 18 …… Discharge port, 32…
... electromagnetic valve, 34 ... time controller (electromagnetic valve control means), 41 ... temperature sensor (temperature detection means), 43 ... temperature controller (electromagnetic valve control means), δ ... thrust direction clearance.

Claims (3)

(57) [Claims] 1. A casing, a drive shaft rotatably supported by the casing, and a tip end extending into the casing and serving as a crankshaft; and a rotatable bearing provided on the crankshaft of the drive shaft via a swivel bearing. An orbiting scroll provided with a spiral wrap on the end plate; and a spiral wrap provided on the casing and forming a sealed space between the end plate and the wrap of the orbit scroll. Fixed scroll, and a scroll-type fluid machine including a fluid suction port and a discharge port provided in the fixed scroll, an electromagnetic valve provided on the discharge port side of the fixed scroll, and the orbiting scroll after starting Solenoid valve control means for controlling the solenoid valve to be in a closed state until a thrust clearance between the fixed scroll and the fixed scroll reaches a predetermined size. Scroll type fluid machine. 2. The scroll-type fluid machine according to claim 1, wherein said solenoid valve control means comprises a time controller for setting a predetermined time after starting. 3. The solenoid valve control means according to claim 1, wherein said solenoid valve control means controls said solenoid valve to a closed state based on a detection signal from a temperature detection means for detecting a temperature of said orbiting scroll or fixed scroll. Scroll fluid machine.