JPH02294579A - Pump for both compressible and non-compressible fluid - Google Patents

Abstract

PURPOSE:To achieve the function of a dehydrating system, e.g. a vacuum defreezer, and the function of a vacuum system through a single pump by a method wherein through alteration of the drive theory of a scroll type volume type pump, a compressible and a non-compressible fluid pump can be selected. CONSTITUTION:A title pump is formed with a link mechanism 20 in which a tooth 3 of a driven scroll 1 is movable in parallel to a tooth 8 of a drive scroll 6, a solenoid 24, a drive motor 14 capable of rotating the drive and driven scrolls 6 and 1 in linkage with each other, and a driven gear 13. By rotating the drive end driven scrolls 6 and 1 in the same direction at the same speed around the center of the basic circle, serving as a rotation center, of an involute by which the drive and driven scrolls 6 and 1 are formed, a volume type pump for compressible fluid serving as an object is formed. A turbo type pump for non-compressible fluid serving as an object is formed in a way that the rotation centers of the drive and driven scrolls 6 and 1 coincide with each other and the drive and driven scrolls 6 and 1 are rotated in the same direction at the same speed, and the two pumps can be selected.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a compressible material used for vacuum thawing and vacuum dehydration.
This invention relates to a pump for both incompressible fluids.

(Prior Art) In conventional vacuum thawing equipment, the dehydration system and the vacuum system have been considered separately. Specifically, when the inside of a sealed tank filled with liquid is drained and then transferred to a vacuum state, the liquid cannot be drained using a -S volumetric vacuum pump. On the other hand, if only a turbo-type centrifugal pump is used, even if drainage can be performed, it is impossible to directly transfer to a high vacuum. As a result, natural drainage or a centrifugal pump dedicated to drainage was used for drainage, and a pump dedicated to vacuuming was used for vacuuming, each of which had an independent control system.

On the other hand, there is an ejector pump that has both dehydration and vacuum functions, but the vacuum level reached by ejector pumps is greatly affected by the vapor pressure of the target liquid at that temperature, so there are limits to its use. (Problems to be Solved by the Invention) Incidentally, a scroll-type fluid pump is known that can suck and discharge compressible fluid (gas) and can be used as a vacuum pump or a compressor. As shown in FIG. 4(a), this scroll-type fluid pump has a pair of scrolls A and B having teeth formed in an involute curve, which are arranged opposite to each other, and one scroll A (fixed scroll). is fixed without rotating, and the other scroll B (orbiting scroll) is made to revolve (orbit) without rotating, and by utilizing the change in volume of the space formed between the mountains of both scrolls A and B, the fluid is It is something that is inhaled and exhaled. The basic movement of conventional scroll-type fluid pumps is rotational operation, so even if the teeth of both scrolls are arranged so that they do not touch each other and are driven, centrifugal force does not work, so the lift of the fluid (liquid) cannot be applied. Therefore, conversion to a turbo pump is impossible.

In addition, in conventional scroll-type fluid pumps, a crank mechanism and a rotation prevention mechanism are used to fix one scroll A and make the other scroll B revolve without rotating. The applicant has previously proposed a scroll-type fluid pump that does not use a mechanism or an anti-rotation mechanism (see Japanese Patent Laid-Open No. 62-248888).

The present invention provides a pump for both compressible and non-compressible fluids, which is based on the scroll-type fluid pump previously proposed by the applicant and is capable of sucking in and discharging both fluid and gas. (Means for Solving the Problems) The present invention provides a scroll-type fluid pump consisting of two scrolls formed by involute spirals arranged with a phase of 180 degrees, in which the teeth of one scroll are in contact with the teeth of the other scroll. It consists of a means for enabling the other scroll to move in parallel until Volumetric pumps target compressible fluids by rotating in the same direction at the same speed, and incompressible fluids by aligning the rotation centers of each scroll and rotating each scroll in the same direction at the same speed. It is configured so that a turbo pump can be selected. (Function) In the present invention, both scrolls are separated by the radius of rotation.
This pump can be used both as a compressible fluid pump that rotates at the same speed in the same direction at a point, and as an incompressible fluid pump that rotates on the same axis by sliding one rotating shaft. be. Specifically shown in FIG. 4, FIG. 4(a) is a schematic diagram of a conventional scroll, FIG. 4 et al.) is a mathematical model thereof,
Furthermore, FIG. 4(C) is a schematic diagram of the scroll of the present invention, and FIG. 4(d) is a diagram of its mathematical model.

FIG. 4(a) shows a state in which the orbiting scroll B is orbiting around the fixed scroll A without rotating. If the center OA of the fixed scroll A is taken as the origin, the center 0 of the orbiting scroll B is It is located at (δ, β) in polar coordinates.

Figure 4 (C) shows a state in which two scrolls C and D having independent rotation axes are rotating in the same direction and at the same speed, and scroll D when the center 0 of scroll C is the origin. The center oe is (δ, 0) in polar coordinates
It is located at

Now, when the two scrolls are horizontally aligned with each other in FIG. 4(a) and the rotation angle is O in FIG. 4(C), the vector in the horizontal right direction is the reference vector, and A- vector A for each scroll of D
-D. Furthermore, one of these reference vectors changes as the scroll rotates or translates.
It shall cause rotation or parallel motion. According to this standard, each reference vector becomes vector bA-b in FIG.

The following explanation will be given according to the mathematical models shown in Figures 4 and 4(d). In FIG. 4, etc., points 0 and i are rotating around point OA without rotation, so the reference vectors bA and bs above them are parallel.

Further, the position of the reference vector b8 is at a position (δ.β) in polar coordinates with respect to the base point OA of the reference vector bA. In FIG. 4(d), both points Oc, O. are rotating in the same direction and at the same speed, the respective reference vectors b and b0 are at positions parallel to each other. Further, the position of the base point OD of the reference vector bD is the reference vector b,
It is located at the position (δ, O) in polar coordinates based on the base point Oc.

In this way, the positional relationship between the reference vector be and the reference vector bD can be expressed by the polar coordinates (δ, 0) as described above, but the reference vector b. If the position of the reference vector b. Let's find the position of the base point OD of by coordinate transformation.

In Figure 4(d), the conversion formula to the new coordinates is only a rotation with respect to the old coordinates, so (1?, θ) = (r, θ) - (0, α)...
・It becomes (1). Here, α is the rotation angle of the new coordinates with respect to the old coordinates. This is the coordinate of the reference vector b0 (δ, 0
), we get (R.θ = (6.0) - (0, - β) = (δ, β)
...(2) becomes. Here, since the rotation angle of the reference vector b is positive in the counterclockwise direction, α=~β is substituted. This is undoubtedly the base point O of the reference vector bl+ obtained by the mathematical model of scrolling in the prior art.
It is equal to the position of the reference vector bA with reference to I with respect to the base point OA (FIG. 4(b)).In other words, the behavior of the scroll of the prior art and the scroll of the present invention are exactly the same as the relative movements of the scrolls. It shows that it is something.

As a result, it is understood that the scroll of the present invention works as a volumetric pump similar to the scroll-type fluid pump of the prior art. Next, when the rotation centers of both scrolls of the present invention are made to coincide with each other, in the case of a conventional scroll type fluid pump, making the centers of each scroll coincide with each other means that the radius of gyration is set to O, It becomes virtually stationary. On the other hand, in the scroll of the present invention, rotational motion occurs even if the axes coincide, and therefore centrifugal force acts on each point of the scroll. Figure 3 shows the component force of the centrifugal force acting on the scroll. It can be decomposed into a component force FC in the tangential direction of the circle, and the fluid has a component force F. This will cause it to be pushed outside the scroll. This is a characteristic of a turbo-type pump, and the scroll-type fluid pump of the present invention functions as a turbo-type pump by aligning the central axes.

As described above, the present invention can be used as a volumetric pump and a turbo pump.

(Example) Hereinafter, one embodiment of the present invention will be described with reference to the drawings.

FIG. 1 shows an exploded perspective view of a pump for both compressible and incompressible fluids according to the present invention.

In the same figure, 1 is a driven scroll, 2 is a disk-shaped back plate, 3 is a spiral tooth formed with an impolite curve, and 4
is a spur gear provided around the side surface of the back plate 2, 5 is a suction/exhaust gear provided at the center of the back plate 2, and this driven scroll 1 has teeth 3 hanging from the back plate 2 to form an involute spiral. .

Reference numeral 6 indicates a main driving scroll; 7 indicates a back plate having the same shape as the above-mentioned back plate 2; 8 indicates spiral teeth formed in an involute curve similar to the above-mentioned teeth 3 and disposed opposite to the above-mentioned teeth 3 with a phase of 180 degrees; Reference numeral 9 denotes a spur gear provided around the side surface of the back plate 7, and the main driving scroll 6 has teeth 8 hanging from the back 17 to form an involute spiral.

10 is the rotation axis of the driven scroll l, 11 is this rotation axis 1
0 is a hollow passage provided at the intake/discharge port 5 of the driven scroll 1.
The transmission gear 9 12 meshes with the main shaft of the main driving scroll 6, and 13 meshes with the spur gear 6 of the driven scroll l and the spur gear 9 of the main driving scroll 6 to synchronize the rotations of both scrolls 1 and 6, and to apply power to the driven scroll l. It is a driven gear that transmits information.

14 is a drive motor that directly or indirectly drives the main shaft 12.
This rotational force is transmitted to the driven scroll 1 via the driven gear 12. 15 is a bearing that rotatably supports the rotating wheel 10, and 16 and 17 are casings. (20) A driving scroll 6 and a driven scroll 1 are disposed in the casings 16, 17, in which the teeth 3 and 8 formed with an involute winding are arranged opposite each other with a phase difference of 180 degrees.

18 is a fluid intake/exhaust port provided in the casing 17;
Reference numeral 9 denotes an opening provided in the side surface of the casing 17, through which the rotating shaft 10 in the casings 16, 17 can be supported from the outside by a bearing 15.

Reference numeral 20 denotes an abbreviated link mechanism for horizontally sliding the driven scroll l, which has a tip hole 2l, a fulcrum hole 22, and a contact protrusion 23, and has a rotating shaft 10 and a bearing 1 fitted therein.
Rotate 5. 24 is a solenoid connected to this link mechanism 20, and when power is applied to the contact protrusion 23 provided at one end of the oval-shaped link mechanism 20, the tip hole provided at the other end rotates about the fulcrum hole 22. The rotating shaft IO connected to 21 slides.

Although the casings 16 and 17 shown in FIG. 1 are shown horizontally long, they are installed vertically when in use. The driven scroll 6 and the upper driven gear 13 of the driven scroll 1 mesh with each other, and the link mechanism 20 can horizontally slide the driven scroll 1.

FIG. 2 is a sectional view of the rotating shaft 10 of the driven scroll 1 of the present invention, and shows the suction, which communicates with the inside of the casings 16 and 17.
A discharge passage is shown.

Reference numeral 25 denotes a bearing case, and the rotating shaft 10 of the driven scroll 1 inserted into the bearing case 25 is rotatably supported by two bearings I5. 26 is a piping nozzle provided in the bearing case 25, and 27 is a bellows that covers the opening 19 of the casing 17, and slidably connects the protruding bearing case 25.

The suction port 5 provided at the center of the driven scroll l is connected to the rotating shaft 1.
0, and this passage l1 has a shunt 28 leading to the piping nozzle 26. The piping nozzle 26 communicates with the rotating shaft 1o and the driven scroll 1,
It communicates with the sealed space between the teeth 8 and 3 between the main scroll 6 and the driven scroll 1. Therefore, the entrance/exit l8 of the casing 17, the inside of the casing IE;, 17, and the intake/exhaust port 5 of the driven scroll l,
The passage 11 of the rotation axis IO, the shunt 28, and the piping nozzle 2
6 are connected. Next, the operation of the embodiment of the present invention will be explained. In the case of turbo type operation, the origins of the two main scrolls 6 and the driven scroll 1, which have teeth 3 and 8 meshing with a phase of 180 degrees, are aligned by operating the solenoid 24, and the drive motor 14 moves the main drive scroll 6. When rotating, the rotational force is transmitted to the driven scroll 1 via the driven gear 13 that meshes with the outer periphery of the two disks, and the main driving scroll 6 and the driven scroll 1 rotate synchronously, at the same speed and in the same direction. Rotate to. For this reason, the piping nozzle 26
, the fluid (liquid) sucked into the sealed section formed by the main scroll 6 and the driven scroll 1 through the shunt 28, the passage 11, and the intake/discharge port 5 of the driven scroll 1. It moves to the outside of the scroll due to the centrifugal force of the rotational movement of the involute spiral, and finally passes through the suction/exhaust port 18 to the casing 16.
, 17.

On the other hand, in the case of compression type operation, that is, the main drive scroll 6 in which the teeth 3.8 of the involute spiral are meshed with each other.
The rotating shaft 10 of one of the driven scrolls 1 and 1 is connected to the link mechanism 2 by operating the solenoid 24.
0 in parallel (perpendicularly in FIG. 1) so that the origin is shifted. At this time, the driven gear 13 continues to mesh even though the origins are aligned (see FIG. 4(C)), and the two main scrolls 6 and the driven scrolls 1 are rotated synchronously.

Further, due to the parallel movement of the driven scroll 1, the teeth 3 of the involute spiral curve move close to the teeth 8 of the main drive scroll 6 with which the teeth 3 mesh so as to come into contact with each other. Contact rotation is performed by opening and closing the narrow space of the teeth 3.8 while creating a sealed space depending on the rotational position, and synchronous rotation is performed in the same direction at the same speed after being shifted by the amount of the slide.

Therefore, it was introduced into the casings 16 and 17. The gas is taken into the sealed space between the teeth 3 and 8 of the involute spiral between the main scroll 6 and the driven scroll 1, moves to the center while being compressed by the involute spiral curve movement, and passes through the suction and exhaust port 5 of the driven scroll 1. and is discharged to the outside from the piping nozzle 26.

Note that in the present invention, the suction side and the discharge side are different between a volumetric pump for gas and a turbo pump for liquid, but the pipe that communicates the piping nozzle 26 with the inlet/outlet 18 It is only necessary to configure the system so that it can be switched appropriately via a switching valve. (Effects of the Invention) As described above, the present invention achieves a compressible fluid pump (a volumetric pump for gas) and a non-compressible fluid pump by modifying the driving principle of a volumetric pump known as a scroll compressor. It is now possible to share a compressible fluid pump (turbo pump for liquids), and a single pump can be used for dehydration and vacuum systems in vacuum thawing equipment, etc.

[Brief explanation of the drawing]

The drawings illustrate an embodiment of the pump for both compressible and incompressible fluids according to the present invention, and FIG. 1 is an exploded perspective view thereof, FIG. 2 is a partially cutaway sectional view of the same essential part, and FIG. 4 is an explanatory diagram of the centrifugal force due to the rotational movement of the scroll, and FIG. 4 is an explanatory diagram of the basic principle. 1...Followed scroll 3, 8...Teeth 6...Main and slave scroll 10...Rotating shaft l2...Main shaft 13...Followed gear 14...Drive motor 16, 17...Casing 20 ... Link mechanism 24 ... Solenoid 5 1 Figure ＼ Ku2 Otsu (a) (b) 63 Juran (c) ＼ D (d)

Claims (1)

[Claims] 1) In a scroll-type fluid pump consisting of two scrolls formed by involute spirals arranged with a phase of 180 degrees, the other scroll can be moved in parallel until the teeth of one scroll come into contact with the teeth of the other scroll. Compression is achieved by rotating each scroll in the same direction at the same speed around the center of the basic circle of the involute that forms each scroll. We selected a volumetric pump that targets incompressible fluids, and a turbo pump that targets incompressible fluids by aligning the rotation centers of each scroll and rotating each scroll in the same direction and at the same speed. A pump for both compressible and incompressible fluids, characterized in that it is configured to be able to.