JPS6221962B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention is characterized in that a worm and a pinion gear provided in a casing mesh with each other to rotate, and a fluid-tight chamber is formed between the tooth surfaces of the casing and worm and the teeth of the pinion gear. This invention relates to a worm-type fluid machine whose volume can be changed.

Conventionally, in this type of fluid machine, a drum-shaped worm having a large number of spiral grooves that meshes with at least one transverse pinion at an external kami is rotatably installed in a fixed casing, and the teeth of the pinion and A fluid-tight chamber is formed between the tooth surface of the worm and the casing, the casing has a fluid inlet and an outlet, and the volume of the fluid-tight chamber is changed by the worm and pinion meshing and rotating. It is structured like this (Special Publication No. 51-31363, etc.). As shown in Figure 1, this conventional type has an axis line A within the fixed casing.
The worm 10 rotating around the worm 10 is meshed with one pinion gear 50 or two pinion gears 50 and 51 arranged in the fixed casing so as to rotate around an axis that intersects the axis A, and the worm The tooth surface of the pinion gear, the teeth of the pinion gear, and the casing form a fluid-tight chamber.
Therefore, the rotating worm 10 and the pinion gears 50, 51 that mesh with the worm have to be formed into external kami eyes, which increases the dimension in the direction perpendicular to the axis A.

That is, if the diameter of the tip of the worm 10 and the diameter of the tip of the pinion gear 50 are equal to d, and the diameter of the bottom of the worm 10 is _d0 , then when there is one pinion gear, the pinion gear and the worm The outer diameter dimension is expressed as 3/2d + 1/2d ₀ , and when two pinion gears are installed in symmetrical positions with respect to the axis A, the outer diameter dimension is 2d + d _0. For example, when the device is used as a compressor, When used, there is a drawback that the dimensions relative to the unit discharge amount per revolution are large.

In addition, as a conventional fluid machine, there is a flat plate-shaped fixed worm with a spiral groove formed on the plate surface, a rotor that rotates around an axis concentric with the worm and perpendicular to the worm surface, and a rotor installed on the outer periphery of the rotor. Some devices are constructed with a pinion gear that rotates together with the rotor and rotates around an axis perpendicular to the rotor axis by meshing with a groove in the worm (U.S. Pat. No. 4,061,449, Japanese Patent Application Laid-open No. 13908/1989). ). In this type, the contact surfaces between the worm and rotor must match precisely to ensure good sealing, but since the rotor rotates by contacting the worm with a three-dimensional curved surface, the contact surfaces between the two It is extremely difficult to process the rotor so that they perfectly match during operation, and there are problems with the sealing between the rotor and the worm and the stability of the rotor's operation.

In view of the above circumstances, it is an object of the present invention to provide a fluid machine that is compact and has stable operation.As shown in principle in FIG. A worm 1 of inner kamiai with a worm tooth surface formed on the side surface, and the worm 1
A cylindrical rotor 2 is provided in the worm 1 coaxially with the longitudinal axis a of the worm 1, and is rotatable relative to the worm 1. It has at least one pinion gear 5 which is rotatable. The worm tooth surface has a plurality of spiral grooves, and the depth of each groove is deepest at the center in the longitudinal direction of the cylinder and gradually becomes shallower toward both ends. On the other hand, a part of the pinion gear protrudes from the outer peripheral surface of the rotor.
The protruding teeth mesh with the grooves of the worm. Thus, the tooth surface of the worm 1 and the pinion gear 5 are rotated by meshing with each other at the inner mesh, and the tooth surface of the worm 1, the teeth of the pinion gear 5, and the outer peripheral surface of the rotor 2 form a fluid-tight chamber. The volume of the fluid-tight chamber is changed by rotating the rotor 2 and pinion gear with the worm 1 fixed, or by rotating the worm and pinion gear with the rotor 2 fixed. It is structured as follows.

If the dimensions of the device of the present invention are expressed according to the above-mentioned FIG. 1, the dimension in the direction perpendicular to the axis a is expressed as 2d-d ₀ as shown in FIG. By the way, the length S of the maximum meshing part between the tooth surface of the worm 1 and the pinion gear 5
If it is the same as the conventional one, the discharge amount per rotation will be the same as that of the conventional one. When the tip circle diameter d of the pinion gear is first determined, the pinion face width and the maximum length S of the pinion gear teeth that mesh with the worm tooth surface to obtain the maximum discharge amount are approximately determined.
The relationship with d ₀ d is limited to about d ₀ ≒0.6d. Applying this relationship to the conventional one and the one of the present invention, in the case of the conventional outer kamiai mentioned above, the minimum dimension when one pinion gear is used is 1.8d, and the minimum dimension when two pinion gears are used. 2.6d, and the minimum dimension when using the conventional disk-shaped worm mentioned above is 2d. On the other hand, in the case of the present invention, the minimum size is 1.4 d whether there is one or two pinion gears, and it is possible to significantly reduce the size while obtaining at least the same discharge amount.

In addition, both the inner surface of the worm and the outer peripheral surface of the rotor have a circular cross-sectional shape and a uniform diameter in the longitudinal direction, making it easy to process and providing a good sealing surface. The operation is stable because it rotates with the outer circumference surrounded by the worm.

A first embodiment of the present invention will be described below with reference to FIGS. 3 to 6.

Reference numeral 1 denotes a worm having a worm tooth surface 101 formed on the inner surface of a fixed cylinder that does not rotate, and also serves as a casing. The worm tooth surface 101 has three spiral grooves P ₁ , P ₂ , P ₃ as shown in the developed view of FIG.
The depth of each groove is deepest at the center in the longitudinal direction of the cylindrical worm and gradually becomes shallower toward both ends. This housing is made up of a plurality of split housings 1a and 1b, for example, split into two in the longitudinal direction for assembly, and these are fixed together with bolts or the like to form the worm 1. 2 is the first axis of the worm 1.
A cylindrical rotor whose outer circumferential surface is in contact with the inner surface of the worm 1 rotates within the worm 1 by the shaft 3 as the axis a of It consists of divided rotors 2a and 2b, which are fixed together with bolts etc., and shafts 3 and 4.
It is fixed integrally with bolts etc.

A pinion gear 5 is disposed within the rotor 2 and is rotatably supported via bearings 17 and 18 around a second axis b that intersects with the first axis a and is offset with respect to the second axis b. . The pinion gear 5 has a gear 501 that meshes with the tooth surface 101 of the worm 1 with an inner kamiai. As shown in Figure 6, the rotor 2 has a slot 2 parallel to the axis.
2 is formed, and the teeth 501 of the pinion gear 5 protrude from this slot 22 in the process of rotation and engage with grooves P ₁ , P ₂ , and P ₃ on the worm tooth surface. A fluid-tight chamber is formed by the tooth surface 101 of the worm 1, the teeth 501 of the pinion gear 5, and the outer periphery of the rotor 2. A casing 6 is coaxially fixed to one side end of the worm 1 and supports the shaft 3 via a bearing 8. Similarly, 7 is coaxially fixed to the other end of the worm 1. The shaft 4 is supported through a bearing 9 by the casing. In the following description of the compressor, numeral 10 is a suction port provided in the case of the worm 1, which communicates with the suction chamber 14, and numeral 11 is an internal discharge port that opens on the rotor surface, leading from the inside of the rotor 2 to ports 12, 13.
and communicates with an external discharge port 16 provided in the casing of the worm 1. The internal discharge port 11 is connected to the teeth 501 of the pinion gear, as shown in FIG.
The slot 22 protrudes from the slot 22 and is open toward the rotor rotation direction in the vicinity of the terminal end of the slot 22.

Next, a case will be described in which the fluid machine of the above embodiment is operated as a compressor. In addition, when operating as an expander, the rotor 2 and pinion gear 5 may be rotated in the opposite direction so that the suction port and the discharge port function in the opposite direction.

When the shaft 3 is rotated around the first axis a in the direction indicated by the arrow f, the rotor 2 integrally fixed thereto is also rotated in the same direction. Along with this, the pinion gear 5, which is meshed with the worm 1 by the inner kami eye, is rotatably supported by bearings 17 and 18 inside the rotor 2, so that it rotates in the same direction as the rotor 2 and simultaneously rotates in the second gear. The worm 1 rotates clockwise (n direction in FIG. 3) around the axis b while maintaining engagement with the worm 1.
Here, the teeth 501 of the pinion gear 5 form a fluid-tight chamber between the tooth surface 101 of the worm 1 and the rotor 2, and when the pinion gear 5 rotates together with the rotor 2 relative to the fixed worm 1, One of the sealed chambers communicating with the suction chamber 14 adjoining the suction port 10 increases in volume to draw fluid into the chamber, which is subsequently closed by the teeth 501 of the pinion gear 5 into the suction chamber. 14 and pinion gear 5
As the chamber rotates, the volume of the chamber is gradually reduced and the liquid is compressed, and the liquid flows through the internal discharge port 11 and outlet port 1.
2, 13 and the discharge chamber 15 to the external discharge port 16
It is discharged even more. To further explain this operation with reference to FIG. 5, the teeth 501 of the pinion gear rotate together with the rotor 2 while meshing with the grooves P ₁ , P ₂ , P ₃ of the worm, thereby forming groove ends P ₁₀ , P ₂₀ and
P ₃₀ (not shown) while compressing the liquid, and sequentially passes through the terminal end. On the other hand, the rotor 2 is formed with one internal discharge port 11 as shown in FIG. Move to. Immediately before the teeth 501 reach the terminal ends of each groove, they pass through while communicating with these terminal ends, and at this time, the compressed liquid in each groove is sequentially discharged from the internal discharge port 11.

Next, a second embodiment of the present invention will be described with reference to FIGS. 7 and 8. Note that descriptions of common parts with the first embodiment will be omitted.

Two pinion gears 5 are provided within the rotor 2, and these gears are connected to the first axis a, which is the axis of the worm 1.
The worm ₁ has six grooves ( _even numbered ). Teeth 50 of both pinion gears 5
1,502 protrude from two slots formed in the rotor 2 and engage with grooves in the worm 1. An internal discharge port 11 is formed in the rotor 2 at a position corresponding to the internal discharge port 11 shown in FIG. 6, close to the end of each slot. As the rotor 2 rotates, these two internal discharge ports 11 pass through the ends of each groove of the worm 1, as in the first embodiment.
The liquid compressed by the teeth 501 of one pinion gear is transferred from one discharge port to the teeth 501 of the other pinion gear.
The liquid compressed in step 02 is discharged from the other discharge port. In the second embodiment, the pressure balance in the radial direction applied to the outer circumference of the rotor 2 is maintained, and the shaft 3,
The bending moments of 4 are canceled out, resulting in more stable operation. Note that the number of pinion gears is not necessarily limited to two, provided that the number of threads on the worm 1 is an even number and the pinion gears are positioned symmetrically with respect to each other as described above. Further, since each pinion gear is located at a position where they do not interfere with each other, the radial size of the device can be made compact.

In all of the above embodiments, the worm 1 is fixed and the rotor rotates, but even if the worm 1 of the inner kamiai is rotated and the member corresponding to the rotor 2 is fixed, the same effect as described above can be obtained. and can be effective. However, in this case, the worm 1 is naturally rotated in the opposite direction to the rotational direction of the rotor 2.

As described above, the worm-type fluid machine of the present invention includes a worm having a worm tooth surface formed on the inner surface of a cylinder, a rotor provided within the worm coaxially with the longitudinal axis of the worm, and capable of rotating relative to the worm. A pinion gear is provided in the rotor and is rotatable around an axis that intersects with the above-mentioned axis and is offset with respect to the axis. This feature makes it possible to significantly reduce the size of conventional devices of this type while achieving the same discharge amount. Furthermore, since the rotor with the pinion gear installed therein is cylindrical and rotated within the cylindrical worm, the rotor can operate stably.

[Brief explanation of the drawing]

Fig. 1 is a schematic diagram of a conventional fluid machine, Fig. 2 is a schematic diagram of a fluid machine of the present invention, Figs. 3 to 5 show a first embodiment of the present invention, and Fig. 3 is a schematic diagram of a fluid machine of the present invention. A vertical sectional view of the first embodiment of the present invention, FIG. 4 is a sectional view along the line - in FIG. 3, FIG. 5 is a developed view of the worm, FIG. 6 is a side view of the rotor, FIG. FIG. 8 shows a second embodiment of the present invention.
The figure is a longitudinal sectional view, and FIG. 8 is a sectional view taken along the line -- in FIG. 1... Worm, 101... Worm tooth surface, 2
... Rotor, 5 ... Pinion gear, 501 ... Pinion gear teeth, 10 ... Suction port, 11 ... Internal discharge port, 12 ... External discharge port.

Claims (1)

[Scope of Claims] 1. A worm having a plurality of spiral grooves formed on the inner surface of a cylindrical body, the depth of which is deepest at the center in the longitudinal direction of the cylindrical body and gradually becomes shallower toward both ends; A cylindrical rotor is installed coaxially within the worm and rotates relative to the worm with its outer peripheral surface touching the inner surface of the worm.A cylindrical rotor is installed inside the rotor and rotates around an axis that intersects with the axis of the worm and is offset from the axis. at least one pinion gear, a part of the outer periphery on which teeth are formed protrudes from the outer periphery of the rotor and meshes with the groove of the worm; A fluid sealed chamber whose volume changes as the gear rotates; a fluid inlet formed in the worm for supplying fluid to the fluid sealed chamber; and a fluid discharge port formed in the worm to discharge fluid from the fluid sealed chamber. A worm type fluid machine comprising: 2. The rotor is provided with a pinion gear rotatable around a plurality of axes that intersect with the axis of the worm and are offset in point symmetry with respect to the axis, and the worm has an even number of grooves. A worm-type fluid machine according to scope 1.