JPH09264267A - Rotary pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve pump efficiency sharply, and suppress discharging pulsation by forming a communicating passage for communicating a discharging port communicated with a pair of discharging operating chambers formed in order in association with rotation of a nearly triangle shaped rotor in a downstream side, and connecting one confluent passage to the downstream end of the communicating passage. SOLUTION: In a triangle shaped rotor 4 rotated through an eccentric collar 3 in a housing 1, four operating chambers are formed between the outer surface formed between top parts 4a to 4c and the trochoid curve 5 of a housing main body 5, namely, first and second intake operating chambers 13a, 13b and first and second discharging operating chambers 13c, 13d which are changed after respective capacities of the operating chambers 13a, 13b are changed into a maximum level, are formed. First and second discharging ports 19, 20 communicated with the discharging operating chambers 13c, 13d are connected through a communicating passage 21, and the downstream end part of the communicating passage 21 is connected to one confluent passage 22. It is thus possible to make the pulsation phase of a fluid discharged from respective discharging ports 19, 20 smoothly by interfering mutually.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary pump used as an oil pump for supplying lubricating oil or hydraulic oil to, for example, internal combustion engines and equipment for automobiles.

[0002]

As is well known, there are various types of oil pumps, such as an internal gear pump and a plunger pump, for supplying lubricating oil to an automobile internal combustion engine or supplying hydraulic oil to a power steering. ing.

Generally, as an automatic internal combustion engine, in addition to a so-called reciprocating engine, four strokes of intake, compression, expansion, and exhaust are continuously performed every one rotation movement while the rotor slides on the trochoid curved surface. A known Wankel type rotary engine is known.
726, etc.).

To explain the outline of this Wankel type rotary engine, side housings are provided on both side surfaces of a rotary housing having a peritrochoidal curved surface on the inner peripheral surface thereof, and a substantially triangular rotor is provided inside the rotary housing. Are rotatably housed while slidingly contacting the peritrochoid curved surface, and three working chambers are formed between the rotor outer peripheral surface and the peritrochoid curved surface. Further, a disc-shaped eccentric portion whose center is eccentric with the axis of the output shaft is integrally provided on a predetermined outer peripheral surface of the output shaft which is a crankshaft penetrating both side housings. The inner peripheral surface of the rotor is supported by the outer peripheral surface. Further, a fixed gear having a small diameter is fixed to the inner peripheral surface of the output shaft through hole of one side housing so as to face the working chamber, and a rotor gear that meshes with the fixed gear is formed on the inner peripheral surface of one end of the rotor. Has been done.

The rotary housing has an intake port and an exhaust port formed in parallel on one side, and a pair of spark plugs mounted on the opposite side.

Then, when the engine is started, the rotor gear meshes with the fixed gear to rotate, whereby the rotor draws a peritrochoid curve which is a basic curve of the rotor housing and makes a rotary motion, while the power is transmitted through the eccentric collar. To the output shaft. That is, as the rotor rotates, the intake port opens and the intake stroke begins,
The intake ports are automatically closed when the volumes of the two working chambers gradually increase and reach the maximum. After that, the air-fuel mixture in the working chamber is compressed, ignited in the vicinity of the compression top dead center, and transferred to the expansion stroke. Next, after passing through the expansion stroke, the exhaust port opens, and after the exhaust stroke is completed, the suction stroke is started again. As a result, the output shaft rotates three times for each rotation of the rotor, and the power is transmitted to the output shaft.

[0007]

Since such a four-stroke, one-cycle rotary engine has a very high power efficiency, it is possible to apply the basic structure of the rotary engine to an oil pump of an automobile or the like in recent years. ing. However, since the rotary engine targets a compressible fluid such as an air-fuel mixture, and is designed to function as an engine depending on the compression stroke or expansion stroke of the compressible fluid, that is, the volume change of the working chamber, non-compression of oil or the like occurs. It is impossible to apply it directly to an oil pump for a sexual fluid. In other words, since it is impossible to compress and expand the incompressible fluid due to a large volume change of the working chamber, it cannot be applied to the oil pump.

[0008]

The present invention has been devised in order to apply the rotary engine to an oil pump, and the invention according to claim 1 is formed on the inner peripheral surface of a housing. A substantially triangular rotor that rotates while its top is in sliding contact with a trochoidal curved surface, a drive shaft that penetrates through the housing and that drives the rotor to rotate through an eccentric cam, and an outer peripheral surface of the rotor as the rotor rotates. And a pair of suction working chambers formed between the trochoid curved surface and the trochoid curved surface, and a pair of suctions respectively communicating with the suction working chambers when the suction stroke is caused by rotation of the rotor. A rotary pump having a port and a pair of discharge ports that communicate with each of the discharge operation chambers when the compression stroke is entered, the communication being for communicating both discharge ports on a downstream side. To form a, it is characterized by connecting a single converging passage to the downstream end of the communication passage.

Therefore, when the rotor rotated along with the rotation of the drive shaft rotates along the trochoidal curved surface and reaches a predetermined rotational position, the two working chambers (suction working chambers) communicate with the suction ports, respectively. Therefore, as the volume of the working chambers for both suctions increases (expansion stroke), incompressible fluid, for example, lubricating oil is sucked into the working chambers for both suctions (suction stroke). Further, the rotor rotates, the suction port is closed, the communication with each suction working chamber is cut off, and a transition is made to the compression stroke, and at the same time, each suction working chamber is converted into a discharge working chamber. Each discharge working chamber communicates with each discharge port. Therefore, the lubricating oil in each discharge operation chamber is quickly discharged to each discharge port (discharge stroke) to perform a series of pumping actions.

That is, since the lubricating oil in each discharge working chamber is sent out to each discharge port at the same time as the shift to the compression stroke, the lubricating oil is pumped by the rotor. The strong compressive action of oil is avoided. This makes it possible to exert the function as an oil pump, and at the same time obtains a double pumping action.

Moreover, the respective lubricating oils discharged from the respective discharge ports join together in the merging passage via the communicating passages, where the lubricating oils having different pulsation phases interfere with each other. Therefore, each pulsation is suppressed and smoothed.

Further, the invention of claim 2 is characterized in that the discharge port is formed by at least two passage holes, and the outlet portions of the discharge ports are arranged at mutually different positions.

Since the respective discharge ports and the respective passages are formed inside the housing, the passages can be easily handled and the manufacturing workability is improved as compared with the case where the discharge ports and the passages are communicated or merged outside the housing.

Further, in the invention of claim 3, the suction port is
It is characterized in that it is formed of a main port formed in the housing and a branch port branched on the downstream side of the main port and connected to each suction working chamber.

Therefore, as in the second aspect of the invention, the passage can be easily handled and the manufacturing workability is improved.

[0016]

1 to 3 show a first embodiment of a rotary pump according to the present invention applied to an oil pump for lubricating an internal combustion engine, in which a housing 1 and an inside of the housing 1 are arranged so as to penetrate therethrough. And a rotor 4 which is rotatably housed inside the housing 1 and is rotationally driven by the drive shaft 2 via an eccentric collar 3.

The housing 1 is composed of a housing body 5 and a cover 6 fixed to one end of the housing body 5 by a countersunk bolt 7 to close the one end opening. The housing body 5 has a substantially rectangular shape and has a drive shaft insertion hole 5a formed at the center thereof.
A cocoon-shaped recess 5b is formed on one end surface of the cover 6, and an inner peripheral surface of the recess 5b is formed on a trochoidal surface 5c. The outer shape of the cover 6 is formed in the same rectangular shape as the housing main body 5, and is positioned on the housing main body 5 during assembly by a positioning pin (not shown).

The drive shaft 2 is directly connected to the crankshaft of an internal combustion engine, and the eccentric collar 3 is fixed to the outer peripheral surface of the drive shaft 2 by a key 8 longitudinally arranged in the outer peripheral groove 2a and has a tip end. The drive pulley 9 is fixed to the portion by a bolt 10 screwed from the axial direction. The drive pulley 9 has a cylindrical portion 9a fitted on the outer periphery of the drive shaft 2 on the inner peripheral portion of the main body, and transmits the rotational force to the drive shaft 2 via a timing belt (not shown). Has become. A seal member 11 is interposed between the inner circumference of the housing body 5 and the tubular portion 9 of the drive pulley 9.

As shown in FIG. 3, the eccentric collar 3 has a cylindrical portion 3a fitted on the outer peripheral surface of the drive shaft 2.
And an eccentric plate 3b integrally formed on the outer peripheral surface of the tubular portion 3a on the drive pulley 9 side, the center P of which is the drive shaft 2.
It is eccentric in the radial direction by an amount e from the axis X of. Further, the tubular portion 3a has front and rear end portions extending to the insertion hole 5a of the housing body 5 and the insertion hole 6a of the cover 6, and a front end portion of the tubular portion 3a at an end edge of the tubular portion 9a of the drive pulley 9 and a rear end portion. The parts are respectively brought into contact with the stepped end faces of the drive shaft 2 for axial positioning. Further, the eccentric plate 3b is arranged in the circumferential direction of a plurality of large and small holes 12 for weight reduction and weight balance.

The thickness of the rotor 4 is set to be slightly smaller than the width of the recess 5b of the housing body 5, and the rotor 4 is provided between the trochoidal curved surface 5c and the outer surface between the tops 4a to 4c.
The two working chambers 13a, 13b, 13c, 13d are formed, and the tops 4a to 4c are always in sliding contact with the trochoid curved surface 5c to draw a peritrochoid curve and perform a rotational movement. Also, the rotor 4
A circular hole is formed in the center of the circular hole as shown in FIG. 1, and the inner peripheral surface 4d of the circular hole is fitted and supported by the outer peripheral surface 3c of the eccentric plate 3b of the eccentric collar 3.

The four working chambers are formed according to the rotational position of the rotor 4 as shown in FIGS. 3 to 5, and are formed on the first suction working chamber 13a and the first suction working chamber 13a on the opposite side. Two
Intake working chamber 13b and the first and second suction working chambers 1
First converted after 3a, 13b undergoes maximum volume change
It is composed of the discharge working chamber 13c and the second discharge working chamber 13d on the opposite side.

Further, between the cover 6 and the rotor 4,
Guide means for rotating and guiding the rotor 4 along the trochoid curved surface 5c is provided. That is, the guide means is provided on the endless guide groove 14 formed on the inner side surface 6b of the cover 6 and one side surface of the rotor 4 on the cover inner side surface 6b, and is fitted into the guide groove 14. It is composed of two guide pins 15.

As shown in FIGS. 1 and 3, the guide groove 14 is notched in a U-shaped cross section on the inner surface 6b of the cover and is formed in an eyebrow shape along the shape of the trochoid curved surface 5c. On the other hand, the guide pin 15 has its base end portion press-fitted and fixed in a fixing hole 16 penetratingly formed at a position corresponding to the guide groove 14 near each of the top portions 4a to 4c of the rotor 4, and the tip end portion 15a is fixed. The guide groove 14 is fitted and arranged with a slight clearance.

The inside of the cover 6 is shown in FIG.
As shown in FIG. 5, a pair of suction ports 17 and 18 are formed. Both of the intake ports 17 and 18 are provided with the cover 6
Are formed so as to face each other on both sides in a substantially horizontal direction, and are slightly offset in the vertical direction. Further, the first suction port 17 on the lower right side of the drawing is such that the tip portion 17a is appropriately communicated with the first suction working chamber 13a formed by the rotation of the rotor 4 within a predetermined range from a predetermined rotation position. In addition, the tip end portion 18a of the second suction port 18 on the upper left side of the drawing is appropriately connected to the second suction working chamber 13b within a predetermined range from a predetermined rotation position. Further, the inlet ends 17b and 18b of the respective suction ports 17 and 18 communicate with the oil pan via a single passage, not shown, which is connected to the respective two passages (not shown) on the upstream side. ing.

Inside the housing body 5a, as shown in FIGS. 1 to 5, a pair of discharge ports 19,
20 are formed. These discharge ports 19, 20
Are formed substantially horizontally in parallel with the suction ports 19 and 20 at opposite positions on both sides of the housing body 5a, and are vertically offset from each other. Second
First discharge port 19 arranged below the suction port 18
Is connected to the first discharge working chamber 13c formed by the rotation of the rotor 4, while the second discharge port 20 disposed above the first suction port 17 is , The tip portion communicates with the second discharge operation chamber 13d.

Further, as shown in FIG. 2, the discharge ports 19 and 20 are connected to the discharge ports 19a and 20a by a communication passage 21, and a single merging passage is provided at the downstream end of the communication passage 21. 22 is connected. That is, the communication passage 21 is bent into a substantially U-shape inside the housing body 5, one end 21a is connected to the discharge port 19a of the first discharge port 19, and the other end 21b is second. The discharge ports 20 are respectively connected to the discharge ports 20a. On the other hand, the merging passage 21 is formed by extending the second discharge port 20, and has the other end 21 of the communicating passage 21 at the upstream end.
b and the discharge port 20a of the second discharge port 20 are connected,
This is the confluence point. In addition, the confluence passage 21
Is connected to the oil main passage of the engine through a pipe (not shown).

Therefore, according to this embodiment, when the drive shaft 2 is rotationally driven via the drive pulley 9, the eccentric collar 3 also rotates synchronously and the rotor 4 via the outer peripheral surface.
To transmit rotational force. Therefore, the rotor 4 is shown in FIG.
As shown in FIG. 5, the guide pin 15 is smoothly guided while sliding in the guide groove 14, and the trochoid curved surface 5c is formed.
Rotate along.

Considering the operation of the rotor 4 in the rotational position from FIG. 3 to FIG. 5, first, in the rotational position shown in FIG. 3, one top portion 4b of the rotor 4 is the tip portion 18a of the second suction port 18. Is closed and the other top 4c is about to open the tip of the second discharge port 20, so that the suction stroke of the lubricating oil from the second suction port 18 to the second suction working chamber 13b ends. And then the second
The suction working chamber 13b is converted into the second discharge working chamber 13d so that the second discharge working chamber 13d is transferred to the second discharge port 20.
Is ready to be discharged (expansion stroke to compression stroke). At the same time, the first suction port 17
Suction of the lubricating oil into the suction working chamber 13a is started.

At this point, the first discharge working chamber 1
The lubricating oil in 3c is discharged to the first discharge port 19, flows into the communication passage 21, and further flows into the merging passage 22 and is pressure-fed from there to the oil main passage.

Further, when the rotor 4 rotates to the rotational position shown in FIG. 4, the volume of the first suction working chamber 13a gradually increases and the working chamber 1 moves from the first suction port 17 to the working chamber 1a.
The lubricating oil is continuously and quickly sucked into 3a, and the suction from the second suction port 18 to the second suction working chamber 13b is started. Further, at this time, the discharge from the first discharge working chamber 13c to the first discharge port 19 is continuously performed, and the lubricating oil in the second discharge working chamber 13d becomes the rotor 4
Is immediately discharged to the second discharge port 20 (the discharge stroke). Therefore, both discharge ports 19, 20
The lubricating oil simultaneously discharged from the first discharge port 19 side flows into the merging passage 22 via the communication passage 21 and directly flows into the merging passage 22 on the second discharge port 20 side, where they join together. To do.

Further, when the rotor 4 rotates to the rotational position shown in FIG. 5, the suction from the second suction port 18 to the second suction working chamber 13b is continuously performed, and at the same time, from the first suction port 17. Suction into the first suction working chamber 13a is also performed, and at the same time, the top portion 4b is at the second discharge port 2
Since 0 is gradually closed, the discharge action to the second discharge port 20 is stopped and the compression stroke is started, but since the first discharge port 19 and the first discharge working chamber 13c communicate with each other, The lubricating oil discharged to the first discharge port 19 flows into the merging passage 22 via the communication passage 21.

Further, when the rotor 4 rotates to the rotational position shown in FIG. 3, the compression stroke of the second discharge working chamber 13d is started, and at the same time, the second discharge port 20 is opened and the discharge stroke is immediately started. Move to.

That is, as the rotor 4 rotates, the intake stroke-expansion stroke-compression stroke-discharge stroke is repeated to perform a series of pumping operations. At the same time when the expansion stroke shifts to the compression stroke, each discharge stroke The working chambers 13c and 13d communicate with the corresponding discharge ports 19 and 20 so that the lubricating oil in the respective discharge working chambers 13c and 13d is discharged into the discharge ports 19 and 20.
It is not discharged to the strong compression action of the incompressible fluid which is the lubricating oil. Therefore, continuous pumping operation is possible.

As described above, according to this embodiment, since the rotary type oil pump can be put into practical use by making some improvements to the basic structure of the rotary engine, the respective working chambers 13a to 13d can be realized. The discharge amount per one rotation of the rotor 4 can be increased as the volume of the pump increases, and the pump efficiency can be improved. That is, each working chamber 1
Since the maximum volume of 3a to 13d is larger than that of other internal gear pumps and the like, the discharge amount per time becomes large. As a result, if the pump capacity is the same as the previous oil pump,
The entire structure can be made sufficiently small, and the pump can be made compact and lightweight.

Moreover, each pair of suction and discharge working chambers 1
Since 3a to 13d and the pair of suction ports 17 and 18 and discharge ports 19 and 20 simultaneously provide a double pumping action, the pump efficiency is further improved, and as a result, the pump can be made more compact and lighter. An excellent pump can be provided.

Moreover, in the present embodiment, as described above, the lubricating oil discharged simultaneously from both discharge ports 19 and 20 merges in the merge passage 22 to interfere with each other and suppress the discharge pulsation. Therefore, the smoothed lubricating oil can quickly flow into the main oil passage.

In addition to the discharge ports 19 and 20, the communication passage 21 and the merging passage 22 are formed in the housing main body 5, so that the piping structure is different from the case where the communication passage and the like are arranged outside the housing main body 5. Can be simplified and made compact.

Further, in this embodiment, the guide groove 14 and the guide pin 15 are used as the guide means of the rotor 4 instead of the gear, so that the structure can be greatly simplified and the number of parts can be reduced.
Therefore, manufacturing work efficiency can be improved and cost can be reduced.

Further, due to the simplification of the structure, the guide groove 14
Therefore, it is not necessary to have a high processing accuracy, and thus the processing efficiency can be improved in this respect as well.

Further, since the guide groove 14 is formed by the notch in the cover 6 and the guide pin 15 is only fixed to the rotor 4, there is no need for a conventional space for mounting a gear. Therefore, the size and weight of the pump can be reduced.

6 to 7 show a second embodiment of the present invention,
The pair of intake ports 23, 24 are connected to the main passage 2 having a substantially L-shape.
It is branched from 5. That is, the main passage 25 includes an upstream portion 25a vertically formed in one side portion of the cover 6, and a downstream portion 25b horizontally extending from an upper end of the upstream portion 25a. The upstream end communicates with the oil pan via a suction pipe (not shown). The one first suction port 23 is horizontally extended from a substantially central position of the upstream portion 25a so that the tip portion 23a communicates with the first suction working chamber 13a, and the other second suction port 23 is provided. The suction port 24 extends downward from the downstream end side of the downstream portion 25b and is bent substantially in an L shape.
The tip portion 24a is adapted to communicate with the second suction working chamber 13b as appropriate.

Therefore, according to this embodiment, the same operation and effect as in the first embodiment can be obtained, and the suction ports 23 and 24 are formed in the cover 6 so as to be branched from the main passage 25. The passage structure is simplified, the manufacturing workability is improved, and the cost is reduced as compared with the case where the respective suction ports divided into two parts are piped outside the cover 6 as in the case of the first embodiment. The cost can be reduced.

The pump of the present invention is not limited to the oil pump as in the above embodiment, but can be applied to a pump for other non-compressible fluid such as water.

The drive shaft 2 may be formed so that the rotational force is transmitted by a timing belt or the like instead of being directly connected to the crankshaft of the internal combustion engine.

It is possible to provide the communication passage 21, the merging passage 22 and the discharge ports 19 and 20 on the cover 6 side, while providing the suction ports 17 and 23 on the housing body 5.

[0046]

As is clear from the above description, according to the rotary type pump of the present invention, the pump having the basic structure of the rotary engine can be put into practical use, and the pump efficiency is greatly improved. Can be improved. As a result, if the pump has the same capacity as before, the pump can be made compact and lightweight.

In addition, since the present invention can simultaneously perform the double pumping action with one pump, the pump efficiency is further improved, and as a result, the above-mentioned compactness and weight saving of the pump can be further promoted.

Further, since the downstream side of the pair of discharge ports is connected to the confluent passage through the communication passage, the incompressible fluids discharged from both the discharge ports merge in the confluent passage and interfere with each other, resulting in mutual discharge pulsation. Will be canceled out. Therefore, large discharge pulsation on the downstream side can be suppressed and smoothed.

Further, according to the inventions of claims 2 and 3,
Since each suction, discharge port, communication passage, confluence passage, etc. are formed inside the housing, the pipes can be routed, that is, the piping structure can be simplified and compact compared to the case where the confluence passage is provided outside the housing. Can be achieved.

[Brief description of drawings]

FIG. 1 is a sectional view showing a first embodiment of a rotary pump of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a sectional view taken along line BB of FIG. 1 showing the operation of this embodiment.

FIG. 4 is a cross-sectional view taken along line BB in FIG. 1 showing the operation of this embodiment.

5 is a sectional view taken along line BB of FIG. 1 showing the operation of this embodiment.

FIG. 6 is a longitudinal sectional view showing a second embodiment of the present invention.

7 is a cross-sectional view taken along the line CC of FIG. The sectional view on the AA line of FIG. 2 which shows the effect | action of a present Example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Housing 2 ... Drive shaft 3 ... Eccentric collar 4 ... Rotor 5 ... Housing body 5c ... Trochoid curved surface 6 ... Cover 13a ... 1st suction working chamber 13b ... 2nd suction working chamber 13c ... 1st discharge working chamber 13d ... second discharge working chamber 17,23 ... first suction port 18,24 ... second suction port 19 ... first discharge port 20 ... second discharge port 21 ... communicating passage 22 ... merging passage

Claims (3)

[Claims] 1. A substantially triangular rotor that rotates while its apex is in sliding contact with a trochoidal curved surface formed on the inner peripheral surface of a housing, and a rotor that is arranged so as to penetrate through the housing and through an eccentric cam to rotate the rotor. The drive shaft, a pair of suction working chambers and a pair of discharge working chambers formed between the outer peripheral surface of the rotor and the trochoid curved surface as the rotor rotates, and when shifting to the suction stroke by the rotation of the rotor. A pair of suction ports respectively communicating with the suction working chambers,
A rotary pump that includes a pair of discharge ports that communicate with each of the discharge operation chambers when the compression stroke is entered, and that forms a communication passage that connects the discharge ports on the downstream side, A rotary type pump characterized in that one merging passage is connected to a downstream end of the communication passage. 2. The rotary pump according to claim 1, wherein the both discharge ports, the communication passage, and the merging passage are formed in the housing. 3. The both intake ports are branched from one main passage, and both intake ports and the main passage are formed in the housing.
The described rotary pump.