JPS63167091A - Compressor - Google Patents

Abstract

PURPOSE:To unify the compression force of fluid and simplify miniaturize a structure and also heighten compression efficiency by providing a spiral inside spiral article at the inner cavity of an outside spiral article provided with a spiral inner cavity and also providing a valve plate covering the opening portion of the discharge opening side of the inner cavity and making a constitution in which a valve body is provided at this valve plate. CONSTITUTION:An outside spiral article 17 rotates together with the rotation of a rotor 16 through the electrification of a motor portion 12, and also an inside spiral article 18 is driven by means of the slide contact operation of the inner cavity 19 of the outside spiral article 17, and revolves while its rotation is being checked by means of a rotation regulating means. By this, the compression operation of fluid can be done almost uniformly and consecutively. Furthermore, the simplification and miniaturization of its constitution can be accomplished by such a constitution as this one. Also, a discharge opening is opened/closed by a valve body 37 provided at a valve plate 21, so there is no re-expansion of compressed fluid, resulting in the non-need of extra drive input, and compression efficiency can be heightened.

Description

[Detailed description of the invention] [Purpose of the invention] (Industrial application field) The present invention relates to a compressor used in a refrigeration cycle or the like.

(Prior Art) Conventionally, there are two types of compressors used in refrigeration cycles: reciprocating type compressors and rotary type compressors. FIG. 14 shows an example of a conventional reciprocating compressor. This reciprocating type compressor is equipped with a cylinder 1 and a piston 2, and the piston 2 has an eccentric shaft 5 provided on a rotating shaft 4 of an electric motor section 3.
and is reciprocated via the connecting rod 6.

(Problems to be Solved by the Invention) The above-mentioned reciprocating type compressor requires many moving members and members for supporting and guiding them, which makes it complicated and large. There are drawbacks. Furthermore, there is a drawback that the number of parts is extremely large and the product is expensive.

Furthermore, the amount of fluid sucked and discharged varies greatly, and the torque required for driving also varies greatly. These problems also apply to rotary one-way compressors.

The present invention has been made in view of the above circumstances, and its purpose is to equalize the compressive force of the fluid and to
It is an object of the present invention to provide a compressor of a type that can be made simple and compact with a small number of parts, and further to prevent re-expansion of gas and improve compression efficiency.

[Structure of the Invention] (Means and Effects for Solving the Problems) In order to solve the above-mentioned problems, the present invention provides an inner helical part having a helical shape in the lumen of an outer helical part having a helical lumen. The two helical parts move relative to each other to transport the fluid from one end of the inner cavity of the outer helical part to the other end, and discharge the fluid from the outlet at the other end. A valve plate is provided to cover an opening on the discharge port side of the inner cavity, and a valve body is provided on the valve plate to open and close the discharge port.

Thus, by relatively rotating the outer spiral component and the inner spiral component, the fluid compression action can be performed substantially uniformly and continuously. Furthermore, the above structure allows the structure to be simplified and downsized. Furthermore, since the discharge port is opened and closed by the valve body, there is no re-expansion of the compressed fluid and no extra drive input is required.

(Embodiment) FIGS. 1 to 9 show a first embodiment of the present invention. This embodiment concerns a hermetic compressor used in a refrigeration cycle as shown in FIG. In Figure 2, 7
8 is a condenser, 8 is an evaporator, 9 is a throttle valve, and 10 is a hermetic compressor.

This hermetic compression 110 is constructed as shown in FIG. That is, the inside 11 is a hermetically sealed case for the compressor main body, and inside this case 11, a motor section 12 and a pressure NR section 13 are installed side by side.

The electric motor section 12 includes a stator 15 having a coil 14 and a rotor 16, and the rotor 16 is rotated by energizing the coil 14. The stator 15 is attached and fixed to the inner surface of the case 11.

The compressor section 13 is composed of a relatively long outer spiral part 17 and an inner spiral part 18, and the outer spiral part 17 has a spiral along its longitudinal axis as shown in FIGS. 4 and 5. A shaped inner cavity 19 is provided, and this inner cavity 19 has an elongated round shape (oval shape) in cross section at each position in the longitudinal axis direction. That is, the lumen 19 has a perfect circular cross-sectional shape at each end on the long diameter side at each position, and the cross-sectional shape at both ends on the short side is a straight line tangent to the perfect circle at both ends. Further, the distance between the center of the perfect circle at both ends and the center 0 of the inner cavity 19 is 2e. Further, the inner cavity 19 is formed so that the direction of its oval shape can be rotated by 360 degrees by one pitch (length 2β). Furthermore, as shown in FIGS. 6 and 7, the cross-sectional shape of the inner spiral component 18 at each position in the direction of its central axis is always the same as the width between the minor walls of the inner cavity 19 at the corresponding location. They are formed into perfect circular shapes with equal diameters. Further, as shown in FIG. 6, the eccentricity of the perfect circle in cross section with respect to the center of the inner helical spiral component 18 is e, and the length of one pitch of the spiral is β.

Further, a head 2 is provided on the suction side end surface of the inner spiral component 18.
0 is provided, and this head 20 is partially in close contact with the suction side end surface of the outer helical component 17 so as to partially open the inner cavity 19. Further, a valve plate 21, which will be described later, is attached and fixed to the other end side of the inner spiral component 18, that is, the end face on the discharge side. This valve plate 21 is also tightly joined to the discharge side end face of the outer spiral part 17. The inner spiral part 1 is connected to the outer spiral part 17 by this head 20 and the valve plate 21.
8 is prevented from moving in the axial direction, while allowing relative rotation between the two. These two spiral parts 17.
18 connects the inner cavity 19 of the outer helical part 17 by uniformly contacting it or by relative rotational movement with a predetermined gap.
It functions to convey fluid from a suction opening at one end to a discharge opening at the other end.

One end portion of this outer spiral component 17 is fitted into a hole 16a formed in the center of the rotor 16 of the electric motor section 12, and is fixedly attached. Also, the outer spiral part.

The other end portion of the main bearing 22 is rotatably fitted into the bearing hole 23 of the main bearing 22 and is pivotally supported. The main bearing 22 is fixedly attached to the case 11, and forms a suction shaft 25 between the main bearing 22 and the case 11. Further, a portion inside the case 11 on the opposite side is formed as a discharge chamber 27.

A suction pipe 28 is connected to a portion of the case 11 corresponding to the suction chamber 25, and a discharge pipe 29 is connected to a portion of the case 11 corresponding to the suction and discharge chamber 27.

Further, the inner spiral component 18 does not rotate but revolves, and is therefore restricted by the following rotation restriction means. That is, the bottle 3 is attached to the head 20.
1 passes through the main bearing 22, and the base end portion of the bottle 31 is pivotally connected to a shaft 32 which is provided upright on the main bearing 22. That is, the rotation of the inner spiral part 18 is prevented by the bottle 31, and the inner spiral part 18 is prevented from rotating by the sliding of the head 20 and the bottle 31.
It allows the revolution of

On the other hand, as shown in FIG. 3, the valve plate 21 is formed into a disk shape so as to cover the entire discharge side opening portion of the outer spiral component 17, and is attached to the discharge side end of the inner spiral component 18.
It is fixed with bolts 35. Further, a discharge hole 36 forming a discharge port is bored in this valve plate 21. This discharge hole 36 is one of the above-mentioned It! It is eccentrically located corresponding to one end in the longitudinal direction of the oval shape of No. 19. In other words, the discharge hole 36 communicates with the inner cavity 19 when one longitudinal end of the oval shape of the inner cavity 19 is positioned when the outer spiral component 17 rotates.

Furthermore, a valve body 37 is provided on the outer surface of the valve plate 21 to open and close the discharge hole 36, as shown in FIG. The valve body 37 and the one-sided retainer 38 are collectively fastened and fixed to the valve plate 21 by the bolts 35 mentioned above. In other words, although this valve body 37 allows fluid to be discharged through its discharge hole 36 to pass through,
It acts as a check valve to prevent anything from flowing backwards.

Thus, in this closed type compression 1fi10, when the rotor 16 is rotated by energizing the electrolytic wall portion 12, the outer spiral component 17 is rotated together with the rotor 16. In addition, the inner helical part 18 is connected to the inner lumen 1 of the outer helical part 17.
9, and revolves while being prevented from rotating by the rotation regulating means described above. That is, the outer spiral part 17 rotates in a fixed position, and the inner spiral part 1
8 revolves, its inner cavity 19 and inner spiral part 1
The closed space S formed between the circumferential surface of the ninth
As shown in the figure, the outer spiral part 17 moves forward in sequence according to the rotation angle, and the fluid confined in this space S is transferred to the suction chamber 2.
5 toward the discharge chamber 27 fill. And inside II! At the discharge end 19, it changes as shown in FIG. In other words, one internal lumen per revolution of the outer helical part 17.
The oval-shaped longitudinal ends A and B of No. 9 oppose the discharge hole 36 twice. Then, the fluid is discharged from one of the outer spiral parts 17.
This is done twice per revolution. Therefore, continuous compression and transfer are performed, and fluctuations in torque during this process are also small. Therefore, the operation of the refrigeration cycle incorporating this compressor 10 is performed smoothly and efficiently, and the operating noise is also low.

Moreover, a valve body 37 having a check valve function is provided on the discharge side,
Since only the fluid to be discharged is passed through and its reverse flow is prevented, there is no re-expansion of the compressed fluid and no extra drive input is required.

By the way, during the above-mentioned compression operation, the valve plate 21 is pressed against the end surface of the outer spiral component 17 by the back pressure P applied from the discharge chamber 27, so that the end surface of the outer spiral component 17 and the valve plate 21 are in close contact with each other. The seal is secured.

Note that, since the high pressure q of the fluid is also applied from the inside of the lumen 19, the pressing force due to the above-mentioned back pressure P is canceled out to some extent, and the thrust force is reduced. In other words, the thrust force applied to the valve plate 21 can be kept small and appropriate.

FIG. 10 shows a second embodiment of the invention. In this embodiment, the outer helical part 17 has cut-out portions 40 for discharge ports at both ends of the oval-shaped longitudinal direction of the inner cavity 19.
40 is formed in the valve plate 21, and a discharge hole 4 is formed in the valve plate 21 so as to correspond to the notch 40.40 at the discharge timing.
form 1.

Normally, the valve plate 21 allows the discharge 1 of the lumen 19 to be
111fi and each notch 40.40 are closed, but at the time of discharge, the discharge hole 41 corresponds to the discharge port notch 40.40, and is opened to discharge the fluid.

11 to 14 show a third embodiment. The valve plate 50 is attached and fixed to the discharge side end face of the outer spiral component 17, and the oval-shaped longitudinal ends of the inner cavity 19 are provided with discharge ports, respectively, as shown in FIGS. 11 and 13. A notch 51.51 is formed. The valve plate 50 is always provided with a discharge hole 52.52, which constitutes a discharge port, so as to correspond to the notch 51.51. Further, on this valve plate 50, a plate-shaped discharge valve 53, which elastically closes each of the discharge holes 52, 52 from the outer surface side at both end portions, is fixed to the valve plate 50 at an intermediate portion by a bolt 54. Note that 55 is a presser foot, which is fixed to the valve plate 50 together with the discharge valve 53 by bolts 54 .

Normally, the valve plate 50 and the discharge valve 53 open the discharge side opening portion of the inner cavity 19 and each notch 8II51.
51 is blocked by rII, but at the discharge timing, the discharge pressure from the discharge hole 52.52 elastically pushes open the plate-shaped discharge valve 53, and the compressed fluid is discharged from the discharge hole 52.52. . Therefore, the discharge valve 53 functions as a tick valve and prevents the compressed fluid from re-expanding as in each of the embodiments described above.

[Effects of the Invention] As explained above, according to the present invention, the number of parts of the compressor section can be significantly reduced, and the configuration can be simplified and downsized. In general, fluid can be pumped continuously and as uniformly as possible during compression operation, and fluctuations in driving torque are also small.

Moreover, since only the fluid to be discharged from the discharge port is passed through and its reverse flow is prevented, there is no re-expansion of the compressed fluid, which improves compression efficiency and eliminates the need for extra drive input.

[Brief explanation of the drawing]

Fig. 1 is a side sectional view of pressure smi according to an embodiment of the present invention;
The figure is a schematic configuration diagram of a refrigeration cycle incorporating compression equipment according to the first embodiment of the present invention, FIG. 3 is a side sectional view of the main parts of the embodiment, and FIG. FIG. 5 is a side sectional view of the outer spiral component in the embodiment, FIG. M6 is a front view of the inner spiral component in the embodiment, and FIG. 7 is the implementation thereof. Side view of the inner helical part in the example, No. 8
The figures also show the order of operation of the outer helical part and the inner helical part in the embodiment, FIG. 9 shows the order of operation of compression by the outer helical part and the inner helical part in the embodiment, and FIG. FIG. 11 is a side sectional view of essential parts showing a second embodiment of the present invention, FIG. 11 is a side sectional view of essential parts in the disclosed example, and FIG. 12 is a side sectional view of a conventional compressor. DESCRIPTION OF SYMBOLS 10... Compressor, 11... Case, 12... Electric motor part, 13... Compressor part, 16... Rotor, 17...
...Outer spiral part, 18...Inner spiral part, 19...
-Inner cavity, 21...valve plate, 25...discharge chamber, 27...
・Suction chamber, 31... bottle, 32... shaft, 36...
・Discharge hole, 37... Valve body, 40... Notch, 52
...Discharge hole. Applicant's Representative Patent Attorney Takehiko Suzue Figure 3 Figure 6 Figure 7 Figure 8 Figure 9 Steel Figure 10 Figure 12 Figure 13 Figure 14

Claims (4)

[Claims] (1) A spiral inner spiral component is disposed in the inner cavity of an outer spiral component provided with a spiral inner cavity, and one end of the inner cavity of the outer spiral component is caused by relative rotational movement between the two spiral components. A mechanism is used for transporting fluid from one side to the other end and discharging the fluid from a discharge port at the other end, and a valve plate is provided to cover an opening on the discharge port side of the inner cavity, and this valve plate has a mechanism for discharging fluid from a discharge port at the other end. A compressor characterized by being provided with a valve body that opens and closes a discharge port. (2) Attach a valve plate to the discharge side end of the inner spiral component to cover the discharge side opening of the inner spiral component, form the discharge port with a hole formed in the valve plate, and The compressor according to claim 1, wherein the discharge port is opened and closed by a valve body attached to a valve plate. (3) A valve plate that covers the discharge side opening of the inner spiral component is attached to the discharge side end of the inner spiral component, and a valve plate that covers the discharge side opening of the inner spiral component is connected to the discharge side end surface of the lumen of the outer spiral component. Claim 1: A discharge notch is formed to serve as a discharge port, and the valve plate itself constitutes a valve body that opens and closes the discharge port by rotation of the outer spiral component. The compressor described in section. (4) Attach a valve plate to the discharge side end of the outer spiral part,
A patent claim characterized in that the valve plate has discharge ports formed at positions corresponding to both long-diameter ends of the inner cavity of the inner spiral component, and the discharge ports are opened and closed by a valve body attached to the valve plate. The compressor according to scope 1.