JPS6220682A - Complex gear type pump - Google Patents

Abstract

PURPOSE:To obtain a tow-throw trochoid pump in small-sized and lightweight form by arranging an annular rotor which has the internal and external gears for the meshing with an external-gear rotor and an internal-gear rotor and carries out pumping action, between the both rotors. CONSTITUTION:The second annular rotor 14 which has a shaft in eccentric position for the shaft of the third rotor 15 and carries out trochoid pump action through the meshing with the internal gear of the third rotor 15 is arranged onto the inner periphery of the third rotor 15 having the internal gears. While, the first rotor 13 which has a shaft in eccentric position for the shafts of the second rotor 14 and the third rotor 15 and carries out trochoid pump action through the meshing of the external gear with the internal gear of the second rotor 14 is arranged on the inner periphery of the second rotor 14. Therefore, the separate pump chambers are formed onto the inner and outer peripheral sides of the second rotor 14, and the function of two units of pumps can be obtained by only one unit of pump, and a two-throw trochoid pump can be made small-sized and lightweight.

Description

Detailed Description of the Invention A1 Object of the Invention (1) Industrial Application Field The present invention is directed to driving a first pump and a second pump at the same time by a single driving source, The present invention relates to a composite tooth pump suitable for forming one fluid pumping system and forming a second fluid pumping system by a second pump.

The composite tooth type pump of the present invention can be suitably employed in various cases where it is necessary to simultaneously generate a continuous fluid flow for a pair of fluid pumping systems in places where there is a strong demand for smaller and lighter pumps. I can do it. For example, when the compound tooth pump of the present invention is used as a lubricating oil pump for a dry sump internal combustion engine, the first pump can be used as a feed pump and the second pump can be used as a scavenging pump.

(2) Conventional technology For example, the method of driving a toothed pump using the driving force of an automobile internal combustion engine and using this toothed pump as a lubricating oil pump to supply lubricating oil to the internal combustion engine is known from Japanese Patent Publication No. 56-27.
This is already known as described in Japanese Utility Model Publication No. 685 or Japanese Utility Model Publication No. 57-24883. In addition, in a dry sump internal combustion engine, the driving force of this internal combustion engine is used to simultaneously drive a pair of lubricating oil pumps, the first of which is used as a feed pump, and the second pump is used as a scavenging pump. It is also already known to use

(3) Problems to be solved by the invention When a pair of toothed pumps are driven by a single drive source,
If a pair of pumps are arranged in series in the axial direction on the same drive shaft, the space occupied by the whole pump will be large in the axial direction, and if a pair of pumps are arranged in parallel in the radial direction with respect to the drive shaft, the space occupied by the whole pump will be large. The space occupied becomes large in the radial direction with respect to the drive shaft, and the driving force transmission mechanism becomes complicated.

However, in the case of lubricating oil pumps for automobile internal combustion engines, for example, there are particularly strict demands for miniaturization and weight reduction. There is a need for a lubricating oil pump that can reduce weight.

Therefore, the main purpose of the present invention is to obtain a composite tooth pump in which the space occupied by the entire pump is small in both the axial and radial directions by organically coupling a pair of pumps coaxially. It is something to do.

B0 Structure of the Invention (Means for Solving 11 Problems) According to the present invention, the outer circumferential portion of the tenth tooth profile and the inner circumferential portion of the twenty tooth profile mesh with each other in an eccentric state. A composite tooth-shaped pump formed by the second pump is obtained by forming the first pump, and by meshing the outer circumference of the tooth profile of the 20th rotor and the inner circumference of the tooth profile of the third rotor in a mutually eccentric state.

(2) Effect When the first rotor is mounted on the drive shaft and rotationally driven by this drive shaft, the outer circumference of the 10th tooth profile and the inner periphery of the 20th tooth profile become eccentric with respect to each other. As a result, the second rotor is driven to rotate, and a pumping action of the first pump occurs between the 10th rotor and the 20th rotor. When the 20th rotor is rotated, the 30th rotor is also rotated at the same time, and the 2nd rotor and the 3rd rotor are engaged with each other in an eccentric state. During this time, the pumping action of the second pump takes place.

(3) Example Below, first, a first example of the present invention will be described. 1 to 3, a cover plate 3 is fixed to the back side of a housing 2 of a pump 1 with a plurality of screws 4, and a cover plate 3 is fixed to the back side of a housing 2 of a pump 1.
It is fixed to the drive source 5 side with an annular seal member 7 disposed on the outer periphery of the drive source 5 interposed therebetween.

A large diameter portion 9 on the base side of the drive shaft 8 protruding from the drive source 5 side is slidably fitted into a circular hole 10 formed in the center of the cover plate 3, and the tip of the drive shaft 8 Side small diameter part 11
protrudes into a circular hole 12 formed in the center of the housing 2. In particular, as shown in Figures 1 and 2,
Chamfered portions 17° 17′ are formed in portions of the small diameter portion 11 that are diametrically opposed to each other, and this double-sided chamfered portion 17
The rotational force of the drive shaft 8 is reliably transmitted to the first rotor 13 because the shaft hole of the first rotor 13 is completely tightly fitted into the small diameter portion 11 having a diameter of 17'.

The inner peripheral part of the first rotor 13 has a shoulder part 16 formed toward the outer surface side of the housing 2, and the outer peripheral surface of this shoulder part 16 can freely come into contact with the inner peripheral surface of the circular hole 12 of the housing 2. is in contact with

A wavy tooth profile is formed on the outer circumferential surface of the first rotor 13, and in particular, in FIG. The inner peripheries of the tooth shapes with wavy tooth shapes are in mesh with each other. Each tooth on the outer periphery of the first rotor 13 is in contact with a tooth profile surface on the inner periphery of the second rotor 14.
The gap formed between the tooth profile on the outer circumference of the second rotor 14 and the tooth profile on the inner circumference of the second rotor 14 increases from right to left in FIG. Therefore, the drive shaft 8 is
When the rotor rotates to the left in FIG. 1 as shown in FIG. The half portion performs the fluid discharging function. This tooth profile meshing system itself is well known in the field of tooth profile pumps.

A wavy tooth profile is also formed on the outer peripheral surface of the second rotor 14, and the third rotor 15, which is eccentric to the right with respect to the second rotor 14 in FIG. The inner peripheral portions of the tooth shapes having wavy tooth shapes are in mesh with each other.

Each tooth on the outer periphery of the second rotor 4 is in contact with a tooth profile on the inner periphery of the third rotor 15, and the tooth profile on the outer periphery of the second rotor 14 and the tooth profile on the inner periphery of the third rotor 15 are in contact with each other. The gap formed between the surface and the surface becomes larger from the left to the right in FIG. Therefore, when the drive shaft 8 rotates to the left in FIG. 1 as shown by arrow A, the second rotor 1
The lower half of the gap between the outer periphery of the tooth profile No. 4 and the inner periphery of the tooth profile of the third rotor 15 performs a fluid suction action, and the upper half performs a fluid discharge action.

The cylindrical outer peripheral surface of the third rotor 15 is held by the housing 2 so as to be able to freely come into contact with the housing 2. Further, an annular shoulder portion 18 is formed on the side surface of the annular base between the toothed inner peripheral portion and the toothed outer peripheral portion of the second rotor 14 toward the outer surface side of the housing 2. is slidably held by an annular shoulder 19 formed on the housing 2 side. 1st
The annular shoulder 16 of the rotor 13 and the annular shoulder 18 of the second rotor 14 facilitate assembly of the first rotor 13 and the second rotor 14, respectively, and
3 and the second rotor 14 about corresponding center lines. However, as shown by the dashed line a in FIG. 3, even if the formation of the shoulder portion 18 of the second rotor 14 is omitted, the outer circumference of the tooth profile of the first rotor 13 and the inner circumference of the tooth profile of the second rotor 14 are It is possible to maintain the center line of the second rotor 14 at a fixed position due to the meshing relationship between the toothed outer peripheral portion of the second rotor 14 and the toothed inner peripheral portion of the third rotor 15.

The housing 2 includes the toothed outer circumference of the rotor 13 and the rotor 1.
Figures 1 and 2 of the gap between the inner periphery of the tooth profile of No. 4 and
An arc-shaped suction chamber 20 whose width gradually widens from the right to the left is formed in alignment with the upper half of the figure.
This suction chamber 20 communicates with a connection port 22 via a guide path 21. Further, the housing 2 has a width that gradually narrows from left to right in alignment with the lower half of the gap between the outer circumference of the tooth profile of the first rotor 13 and the inner circumference of the tooth profile of the second rotor 14. An arc-shaped discharge chamber 23 is formed, and this discharge chamber 23 communicates with a connection port 25 via a guide path 24 . Furthermore, the housing 2 has a gap portion between the toothed outer circumferential portion of the second rotor 14 and the toothed inner circumferential portion of the second rotor 14, which is aligned with the lower half in FIGS. 1 and 2. An arc-shaped suction chamber 26 whose width gradually widens from left to right is formed, and this suction chamber 26 communicates with a connection port 28 via a guide path 27 . The arc shape is aligned with the upper half of the gap between the outer circumference of the tooth profile of the second rotor 14 and the inner circumference of the tooth profile of the third rotor 15, and has a width gradually narrowing from the right to the left. A discharge chamber 29 is formed,
This discharge chamber 29 communicates with a connection port 31 via a guide path 30.

Next, the operation of the first embodiment shown in FIGS. 1 to 3 will be explained.

Since the compound tooth type pump is configured as described above, when the drive shaft 8 rotates counterclockwise in the direction of arrow A, the first rotor 13 rotates counterclockwise, and at the same time, the tooth profile of the first rotor 13 and the tooth profile of the second rotor 14 rotate. The second rotor 1 through engagement with the inner circumference
4 rotates to the left, and the third rotor
The rotor 15 also rotates to the left. At this time, the rotation center lines of the first rotor 13, the second rotor 14, and the third rotor 15 are always maintained at constant positions with respect to the housing 2.

Therefore, when the connection ports 22, 28 are in communication with the fluid reservoir, and the connection ports 25, 31 are in communication with the fluid supply destination, as the drive shaft 8 rotates to the left in the direction of arrow A, , in the first fluid pumping system, the fluid is supplied to the connection port 22
, the guide path 21, and the suction chamber 20, and are sucked into the upper half of the gap between the outer circumference of the tooth profile of the first rotor 13 and the inner circumference of the tooth profile of the second rotor 14. While the lower half of the chamber is pressurized, the discharge chamber 23 and guide path 2
4. The fluid is fed under pressure through the connection port 25 to the fluid supply destination. At the same time, in the second fluid pumping system, the fluid passes through the connection port 28 , the guide path 27 , and the suction chamber 26 and enters the gap between the outer circumference of the tooth profile of the second rotor 14 and the inner circumference of the tooth profile of the third rotor 15 . After being suctioned in the lower half of the gap, the fluid is pressurized in the upper half of the gap, and is then forced through the discharge chamber 29, the guide path 30, and the connection port 31 to the fluid supply destination.

FIG. 4 shows a second embodiment of the composite tooth pump of the present invention. In the compound tooth type pump shown in FIG. 4, the third rotor 15' is eccentric to the left in FIG.
A suction chamber 2 is located opposite to the upper half of the gap between the outer circumference of the tooth profile of the rotor 14' and the inner circumference of the tooth profile of the third rotor 15'.
6' is formed, and a discharge chamber 29' is formed opposite to the lower half of the cavity. And the first
The first pump suction chamber 20' is formed between the rotor 13' and the second rotor 14', and the second rotor 14' and the third
The suction chamber 26' of the second pump formed between the rotor 15' and the rotor 15' are both located in the upper half of the compound toothed pump in FIG. The connecting port 22' communicates with the suction chamber 26', and the guide path 2
The connection ports 28' communicating through the pump 7' are both disposed above the compound tooth pump, and the discharge chamber 23' of the first pump and the discharge chamber 29' of the second pump are both connected to the fourth pump. In the figure, the connection port 25' is located in the lower half of the compound tooth pump, and is connected to the discharge chamber 23' through the guide passage 24' and the discharge chamber 29' through the guide passage 30'. The ports 31' are both arranged in the lower position of the compound tooth pump. Other detailed configurations for the radially inner first pump and the radially outer second pump to function as pumps are the configurations of the composite tooth pump shown in FIGS. 1 to 3. is basically the same.

In the compound tooth type pump shown in FIG. 4, both the second rotor 14' and the third rotor 15' are connected to the first rotor 13'.
It is eccentric in the same direction as the first one, that is, to the left in FIG. Second pump discharge chamber 23', 29
' are in the same direction, so those chambers 23' and 29'
are synchronously maintained at high pressure to reduce fluid leakage from the fluid pumping system from the first pump to the second pump.

FIG. 5 schematically shows an example in which the composite tooth pump of the present invention is applied to a lubrication system of a dry sump type automobile internal combustion engine. A drive shaft driven by the engine body 32, for example, the crankshaft of the engine body 32, directly drives the first rotor of the compound tooth type pump of the present invention as shown in FIGS. 1 to 4. , the first pump constituted by the 10th pump and the 20th pump disposed radially outward from the first rotor is schematically shown as a feed pump 34, and the 20th pump is A second pump constituted by a second rotor and a third rotor disposed radially outward from the 20th rotor is schematically shown as a scavenging pump 35. Here, since the second pump is located further outward in the radial direction than the first pump, it has a larger capacity, and when the composite tooth pump of the present invention is applied to a dry sump internal combustion engine It is preferable to use the first pump as a feed pump and the second pump as a scavenging pump as shown in FIG.

The lubricating oil in the oil tank 36 is sucked by the feed pump 34 through an oil path 37 and is forcefully fed through an oil path 38 to an oil filter 40 provided with relief pulp 39. Excess pressure oil in oil passage 38 is removed from oil passage 41 and relief pulp 4.
2 to the oil passage 37. oil filter 40
The lubricating oil that has passed through is sent to the drive system oil lubricating section 33 in the engine body 32 via an oil path 43 and a check valve 44. The lubricating oil that has lubricated the drive system oil lubricating section 33 temporarily accumulates in the oil pan 45, but immediately flows through the strainer 46 and the oil passage 47.
The lubricating oil sucked into the scavenging pump 35 via the scavenging pump 35 and pumped by the scavenging pump 35 returns to the oil tank 36 via an oil passage 48, an oil cooler 49, and an oil passage 50. The oil tank 36 is equipped with an oil level gauge 51.
If the lubricating oil in the oil tank 36 becomes excessive as measured by the above, the excess oil at that time is discharged from the oil tank 36 via the oil drain hose 52.

A portion of the cooling water pumped by a water pump 53 driven by the driving force of the engine body 32 is sent to an oil cooler 49 via a pipe 54.
After cooling the lubricating oil passing through the oil passage 48 at 9,
The water is returned to the water pump 53 via a pipe 55.

The other part of the cooling water pumped by the water pump 53 passes through the cooling passage of the engine body 32, and then passes through the pipe line 56,
The water is returned to the water pump 53 via the radiator 57, thermostat 60, and pipe line 62.

In addition, in the figure, 58 is a reserve tank, 59 is a cooling fan, and 61 is a heater.

In FIG. 5, the first
Since the capacity of the second pump constituting the scavenging pump 35 is larger than that of the second pump, the lubricating oil in the oil pan 45 is not excessively accumulated (the strainer 46, the oil passage 47 It is discharged to the outside of the engine body 32 through.

Effects of the C0 Invention As described above, according to the present invention, the first pump is driven by the fact that the outer peripheral part of the tenth tooth profile and the inner peripheral part of the twenty tooth profile mesh with each other in an eccentric state. A composite tooth-shaped pump is obtained in which the second pump is formed by the outer circumference of the tooth profile of the 20th rotor and the inner circumference of the tooth profile of the third rotor being engaged with each other in an eccentric state. When simultaneously pumping fluid into the system, there is no need to use a pair of independent pumps, and the 10th, 20th, and 3rd rotors are driven in conjunction with a single drive shaft. When simultaneously pumping fluid to two fluid pumping systems using a single drive source, there is no need to arrange a pair of pumps in series or in parallel, and the pump is extremely large in both the axial and radial directions. It is possible to obtain a composite tooth type pump that does not require an occupied space, can keep the outer diameter of the entire pump portion small, has a simple internal structure, and can reduce the weight of the entire pump.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of a composite tooth pump according to a first embodiment of the present invention, FIG. 2 is a cross-sectional view of the composite tooth pump of FIG. 1 in a different position from that in FIG. 1, and FIG. is I-I in Figure 1
[[A vertical cross-sectional view of the main part of the composite tooth pump as seen along the line, FIG. 4 is a cross-sectional view of the composite tooth pump based on the second embodiment of the present invention, and FIG. 5 is a cross-sectional view of the composite tooth pump of the present invention. 13.13';14,14' , 15.15' is a schematic diagram for explaining the fluid flow path system when applied to an automobile dry sump internal combustion engine
...First. Second. 30th evening, 16.18... Annular shoulder, 23.23';29,29'... Discharge chamber,
34...Feed pump, 35...Scahenging pump Patent applicant Honda Motor Co., Ltd. Figure 1

Claims (6)

[Claims] (1) The outer circumference of the tooth profile of the first rotor (13, 13') and the second
A first pump is formed by meshing the toothed inner circumferential portions of the rotors (14, 14') with each other in an eccentric state, and the toothed outer circumferential portions of the second rotors (14, 14') and the third rotor ( 15, 15') are engaged with each other in an eccentric state to form a second pump. (2) On the side surface of the annular base between the tooth-shaped inner peripheral part and the tooth-shaped outer peripheral part of the second rotor (14, 14'), an annular shoulder part (14, 14') concentric with the second rotor (14, 14') 18) is formed, and this shoulder portion (18) allows the second rotor (1
4, 14') are regulated to rotate around a predetermined rotation center line. (3) The first rotor (13, 13') may also
, 13') is formed with an annular shoulder (16) concentric with the toothed pump according to claim 2. (4) The discharge chamber (23, 23') of the first pump and the discharge chamber (29, 29') of the second pump are formed in the same direction when viewed from the center of the pump. A composite tooth pump according to claim (1). (5) The eccentric direction of the second rotor (14, 14') with respect to the first rotor (13, 13') and the second rotor (14, 14') of the third rotor (15, 15')
The eccentric direction of claim No. (
1) Compound tooth type pump described in item 1). (6) The pump is a lubricating oil pump for a dry sump internal combustion engine, and the first pump is a feed pump (34), while the second pump is a scavenging pump (35). A compound tooth pump according to scope item (1).