KR100919788B1 - Pump improved friction resistance of carrier - Google Patents

Abstract

PURPOSE: A booster pump with improved frictional resistance of the carrier is provided to prevent crash noise when a roller enters and leaves the arranged area of the carrier by forming a buffering unit in the arranged area of the carrier in which the roller is arranged. CONSTITUTION: A booster pump with reduced crash noise of a carrier comprises a pumping part, a flow chamber, and a housing. The pumping part includes a cylinder, a carrier, an operation member, a first plate, and a second plate. The cylinder has an eccentric bore. The carrier(142) is located at the bore of the cylinder and sucks and discharges the working fluid. The operation member is arranged within the carrier. The first plate is arranged at the front side of the cylinder and provides a flow path of the sucked working fluid and is integrally coupled with the cylinder. The second plate is arranged at the rear side of the cylinder and provides the flow path for discharging the sucked working fluid. The working fluid flows in and is discharged from the flow chamber in the tangential direction against the rotational direction of the pumping part. The motor for supplying the torque to the pumping part is built in the housing and the housing is segmented with the flow chamber.

Description

PUMP IMPROVED FRICTION RESISTANCE OF CARRIER}

The present invention relates to a pressurized pump having improved frictional resistance of a carrier, and more particularly, a contact area between a carrier disposed in a bore of a cylinder and rotating through a housing, and the first and second plates provided with the carrier interposed therebetween. The present invention relates to a pressurized pump having improved frictional resistance of a carrier capable of reducing the performance and maintenance costs of the pressurized pump by reducing the frictional resistance.

About the pressure pump,

Republic of Korea Patent No. 10-0573800 (2006.04.2006, registered, hereinafter referred to as 'advanced technology') various technologies such as "external pump for side flow type LLP" is presented,

The prior art relates to a pump which can improve suction efficiency by a configuration in which the suction direction of the working fluid coincides with the rotational direction of the pump while allowing the working fluid to pass through the pump.

Here, when the rotor rotates by the motor of the housing, and the roller disposed in the rotor enters the cylinder in accordance with the rotation of the rotor in the bore of the cylinder, the impact is generated as well as the noise caused by the impact as well as wear And damage, etc., resulting in shortening the lifespan of components, degrading performance, and increasing maintenance costs.

In addition, the above factors also occur in the contact surface between the rotor and the cylinder.

In addition, a significant frictional load is generated on the contact surface between the rotor and the cylinder, which causes a problem such as deterioration of performance and leakage of the working fluid into the coupling gap.

In addition, as a known technology related to a volumetric pump, in particular, a vane pump, in which a compression space is moved in accordance with rotation of a pump rotor (in the present invention, referred to as a 'carrier'),

Patent Publication No. 2001-0039353 (May 15, 2001) `` Rotor structure of vane feed pump '' and Patent Registration No.0505821 (July 26, 2005) `` Volume pump ''

In the known pump, the vanes (or rollers in the case of Patent No.0505821) vary the relative distance between the inner surface of the cylinder and the center of the rotor having the centrifugal force generated by the rotation of the rotor and the bore eccentric to the shaft according to the rotation of the rotor. (Or the relative distance to the inner surface of the cylinder having a cylindrical bore is changed by the cam itself movement as the rotor itself), the vane in the mounting groove of the rotor is in a radial direction in the radial direction The inner surface and outer surface of the rotor, the cover plate provided in the front and rear of the cylinder, and the compression space formed by the two vanes are moved and the volume is changed to generate the suction and discharge forces for the fluid.

On the other hand, Patent Registration No. 0462744 (2004.12.10) `` Vacuum Pump for Automobile '' has vanes arranged in the groove of the rotor with tension springs.

In Patent Publication No. 2001-0039353 and Patent Registration No. 0555821, a technique is disclosed in which the vane's linear motion can be reinforced by elasticity of the spring, compared to the vane simply performing a linear motion by centrifugal force.

Although it is true that the performance of the linear motion of the vanes is improved as compared to the Patent Publication Nos. 2001-0039353 and 0,0505821, the organic appearance of the vanes and the vanes is not completely guaranteed.

On the other hand, the patent registration No. 055881 proposes a structure in which the pumping part and the shaft of the motor are used in common, but it does not provide a sealing structure that separates the motor and the pumping part from the fluid. .

In addition, Patent Registration No. 0573800 (2006.04.18) 『External type pump for side flow type LPI』 presents a structure that allows the use of Elpig, which is used as fuel of a vehicle, as a refrigerant for cooling the rotating power supply, that is, a single shaft. Is a shared structure for the motor (referred to as "rotary power supply" in the patent) and the pumping part (referred to as "fluid transfer part" in the patent), and fluid is sucked in and discharged in a tangential direction with respect to the rotational direction of the shaft. The motor and the pumping part are separated by the sealing member.

However, considering the situation in which the motor rotates at high speed and heat is generated in the patent, it is necessary to introduce a sealing member that can more completely block the motor leakage of fluid and for a long time. This is more urgent considering the case where the pumping fluid is a strong acid, a strong salt, or a flammable fluid such as LLP and LENG.

The prior art proposed in order to solve the above problems is the patent registration No. 0736933 (announcement date July 06, 2007),

Although the above-mentioned problems of the prior art have been solved, the assembly of the sharing shaft and the carrier is not easy, and thus the assemblability is remarkably degraded.

That is, there is a problem in that assembly is remarkably inferior as the electric pins for interlocking linear movement of the vanes after pre-assembling the sharing shaft and the carrier are coupled through the fitting portions formed in the sharing shaft and the carrier.

In addition, a conventional pressure pump (or a device equipped with a pressure pump, etc.) is not provided with a means for reducing noise or vibration,

In a place where the pressure pump is installed and operated, there is a problem that may provide an uncomfortable environment, and this may cause a safety accident, especially in the workplace.

In addition, in Patent No. 07369384, any one vane symmetrically arranged on the carrier and the other vanes positioned opposite to each other are formed in such a manner that the inner surfaces of the vanes are supported by one electric pin so that one vane is concealed inside the carrier. The driving pin is pushed along, so the other vanes of the opposite side are exposed to the outside, and the mutually interlocking structure is related to a pressurized pump that assists the vane linear motion by centrifugal force.

In this case, the prior art is a structure provided with a transmission means (that is, a driving pin) for assisting the linear movement of the vane, the assembly is dropped by the transmission means to lower the productivity, as well as severe noise generation problems There was this.

Therefore, the present applicant has developed an improved pressure pump that removes the transmission means, that is, the inlet and outlet of the working fluid can be made only with vanes.

At this time, when the vanes arranged in the carrier is linear movement only by the centrifugal force according to the rotation of the carrier to solve the inferior contact with the inner wall of the cylinder bore,

By forming the complementary passages on both sides of the vanes, that is, the sides corresponding to the contact surface with the fitting groove of the carrier,

The working fluid introduced through the flow channel fills the space from the fitting groove to push the back of the vane to improve contact with the inner wall of the cylinder bore.

Furthermore, various prior arts, such as Patent No. 10573800, relate to a pump capable of improving suction efficiency by a configuration in which the suction direction of the working fluid and the rotation direction of the pump coincide with each other.

In addition, the prior art is that the plate and the cylinder coupled to the shaft is made of a separate type, as well as the assemblability between each component constituting the puncture portion is deteriorated, thereby causing a decrease in productivity and a cost increase.

In addition, when the rotor rotates by the motor of the rotational force supply unit and the roller disposed in the rotor enters and exits with the rotation of the rotor in the bore of the cylinder, an impact is generated, and at this time, the noise is not only generated due to the impact. Abrasion and damage are caused, resulting in shortened parts life, reduced performance, and increased maintenance costs.

In addition, the above factors also occur in the contact surface between the rotor and the cylinder.

In addition, a significant frictional load is generated on the contact surface between the rotor and the cylinder, which causes a problem such as deterioration of performance and leakage of the working fluid into the coupling gap.

In addition, abrasion and damage may occur due to the frictional resistance generated between the rotor disposed in the bore of the cylinder and the first and second plates provided to interpose the rotor, and may act as a factor in deterioration of the pressure pump. In addition, there is a problem that the maintenance cost increases.

The present invention provides a pressurized pump having improved impact noise of a carrier having an elastic buffer member or a buffer layer coated with a buffer material on one or each of the rollers and the carrier to prevent a collision noise between the carriers. For the purpose of

In another aspect, the present invention provides a pressurized pump having an improved impact noise of the carrier that can prevent the collision noise between each other by forming a cushioning material layer having an elastic buffer member or coated with a cushioning material in any one or each of the cylinder and the carrier. It aims to do it.

Furthermore, an object of the present invention is to provide a pressurized pump having a knurled portion formed on a carrier to reduce frictional resistance between the carrier and the cylinder, as well as to minimize a gap between the carriers and to prevent a leakage of fluid, thereby improving a pressure noise of the carrier. It is done.

Furthermore, the present invention is to improve the assembly structure by improving the coupling structure of the carrier and the shaft in the conventional volumetric pressure pump to improve the inconvenience of the conventional coupling of the carrier and the shaft.

Accordingly, the present invention improves the fitting portion formed on the shared shaft in the conventional volumetric pressure pump, so that the electric pin exposed to the shaft coupling portion of the carrier can be easily coupled to the fitting portion of the shared shaft, thereby increasing assembling and disassembling. It is an object of the present invention to provide a volumetric pressurized pump which is easy to maintain and easy to maintain a coupling structure of a shared shaft and a carrier.

In addition, the present invention is made of a shape corresponding to the coupling structure of the driving pin fitting portion can correspond to the number and coupling structure of the driving pin is appropriately selected according to the purpose of use and pump capacity of the shared shaft and the carrier is more extended It is an object of the present invention to provide a volumetric pressure pump with improved coupling structure.

In addition, the present invention eliminates the transmission means such as a power pin or a power spring for the linear motion of the vanes arranged in the carrier in the pressure pump is provided with a separate or integral motor and pumping unit and the vanes and the carrier in the linear motion of the vanes The purpose of the present invention is to provide an improved pressure pump in which a complementary flow path that can replace the power transmission means is formed on both sides of the vane, that is, the surface in contact with the fitting groove of the carrier, in order to improve the contact force with the cylinder. do.

In addition, an object of the present invention is to provide an integral pump of the shaft through plate and the cylinder can be expected to be assembled and productivity by integrally forming the plate and the cylinder coupled to the shaft of the motor unit.

In order to solve the above-mentioned problems, the pressure pump is improved frictional resistance of the carrier,

A cylinder having an eccentric bore, a carrier disposed in the bore of the cylinder, a carrier for sucking and discharging a working fluid, a roller disposed within the carrier, and a working fluid disposed on the front side of the cylinder, A pumping part including a first plate providing a flow path, and a second plate disposed at a rear side of the cylinder and providing a flow path for discharging the sucked working fluid;

A flow chamber in which a working fluid flows in and out in a direction tangential to a rotation direction of the pumping part; And

In the pressure pump comprising a; a motor is built in for supplying a rotational force to the pumping portion, the housing is formed partitioned with the flow chamber,

And reducing means for reducing frictional resistance between the first and second plates and the carrier.

Here, the reducing means is characterized in that the first groove portion is formed in the contact area of the carrier with respect to the first and second plates.

Alternatively, the reducing means is characterized in that the second groove portion is formed in the contact area of the first and the second plate with respect to the carrier.

And it characterized in that it further comprises a first buffer means for preventing collision noise in the contact between the roller and the carrier.

In addition, it characterized in that it further comprises a second buffer means for preventing collision noise in the contact between the cylinder and the carrier.

Finally, an outer circumferential surface of the carrier is characterized in that it is provided with a knurling portion for reducing friction load with the cylinder and minimizing the gap therebetween.

Pressurized pump with improved impact noise of the carrier according to the present invention,

By providing a cushioning means in the arrangement area of the roller and the carrier on which the roller is arranged, collision noise can be prevented when the roller passes through the arrangement area of the carrier,

In addition, by providing a buffer means in the space in which the carrier and the carrier rotates, that is, the cylinder bore, it is possible to prevent the collision noise caused by the rotational movement of the carrier,

And by placing a knurled portion on the outer circumferential surface of the carrier to reduce the frictional resistance between the carrier and the cylinder as well as to minimize the gap between each other to prevent the leakage of fluid,

Due to the effects as described above there is an effect that can be expected to improve the performance of the pressure pump and the competitiveness in the market.

In addition, the pressurized pump according to the present invention has a form in which one shaft is shared while introducing a motor and a pumping portion into one housing, and the shaft is inserted into a carrier embedded in a cylinder forming a pumping portion and having a bore eccentric with respect to the shaft. In this case, the assembly structure is improved by improving the coupling structure of the shaft and the carrier, and the biggest advantage of easy disassembly and easy maintenance is to form a fitting portion corresponding to the coupling structure of the driving pin coupled to the carrier. Has the effect of being more extensible.

Furthermore, the present invention eliminates the transmission means such as a power pin or a power spring for the linear motion of the vanes arranged inside the carrier in the pressure pump provided with a separate or integral motor and pumping unit and the vanes and the carrier in the linear motion of the vanes In order to improve the contact force with the cylinder is accommodated can be provided an improved pressure pump formed on both sides of the vane, that is, the surface in contact with the fitting groove of the carrier to replace the transmission means.

In addition, the integrated pump of the shaft through plate and the cylinder according to the present invention relates to the integrated pump of the shaft through plate and the cylinder, and more particularly, the first coupled to the shaft of the motor portion of the first and second plates in close contact with the front and rear of the cylinder. By forming one plate integrally with the cylinder, there is the greatest effect that can be expected to improve the assembly, productivity and cost reduction due to the reduction of the number of parts.

1 is an exploded perspective view showing a pressure pump according to the present invention,

Figure 2 is a perspective view and a sectional view showing the main pumping portion in the pressure pump according to the present invention,

3 is a cross-sectional view showing a flow chamber in the pressure pump according to the present invention,

4 is a cross-sectional view showing a pump in a pressure pump according to the present invention,

5 is a perspective view showing an example of the first buffer means in the pressure pump according to the present invention;

Figure 6 is a perspective view showing a first buffer means of another example in the pressure pump according to the present invention,

7 is a perspective view showing an example of the second buffer means in the pressure pump according to the present invention;

8 is a perspective view showing a second buffer means of another example in the pressure pump according to the present invention,

9 is a perspective view showing the knurled portion of the carrier in the pressure pump according to the present invention,

10 is a side sectional view showing an example of reducing means in the pressure pump according to the present invention;

11 is a perspective view showing another example of reducing means in the pressure pump according to the present invention.

12 is a schematic exploded perspective view of a pressure pump according to the present invention.

Figure 13 is a schematic coupling cross-sectional view of the pressure pump according to the present invention.

14 is a schematic external view of a pressure pump according to the present invention;

15A is an exploded perspective view of a carrier and a shared shaft of a pressure pump pumping unit according to the present invention;

Figure 15b is a front sectional view showing the pumping portion of the pressure pump according to the present invention.

16 is an exploded perspective view showing another embodiment of a carrier and a shared shaft according to the present invention.

17 is a cross-sectional view of the coupling between the cylinder and the first and second plates forming the pumping portion of the pressure pump according to the present invention.

18 is a perspective view showing a coupling state of the carrier and the vane according to the present invention.

19 is a perspective view showing a coupling state of the carrier and the cylinder according to the present invention.

20 is an exploded perspective view showing an example of a separate type of the pressure pump according to the present invention;

Figure 21 is an exploded perspective view showing a separate type of another example of the pressure pump according to the present invention,

22 is an overall cross-sectional view showing a separate type of the pressure pump according to the present invention,

Figure 23 is an exploded perspective view showing the integral type of the pressure pump according to the present invention,

24 is an overall cross-sectional view showing an integrated type of the pressure pump according to the present invention,

25 is a perspective view showing that a complement flow path is formed in a vane in a pressure pump according to the present invention;

26 is a plan sectional view showing an operating state of the pressure pump according to the present invention;

27 is a view showing a linear motion action through the complement flow path of the vane in the pressure pump according to the present invention.

28 is an exploded perspective view showing a motor portion and a pumping portion and an example working fluid transfer means of the pump according to the present invention;

29 is an exploded perspective view showing another working fluid transfer means in the pump according to the present invention.

30 is an exploded perspective view showing another example of the working fluid transfer means in the pump according to the present invention.

31 and 32 are perspective views showing a first buffering means for a carrier with one or another working fluid transfer means in a pump according to the invention;

<Description of reference numerals for the main components in the drawings of the first group (FIGS. 1 to 11)>

110: flow chamber

120: housing

140: pumping part

141: first plate 142: carrier

143: roller 144: cylinder

145: second plate

300, 400: first and second buffer means

310, 410: buffer member 320, 420: buffer layer

500: knurled part

600: abatement means

610: the first groove 620: the second groove

<Description of main components in the drawings of the second group (FIGS. 12 to 19)>

P: Pump 10: Housing 11, 13: Receptacle 11a, 13a: Cover

12: boundary 15: inlet 17: outlet

20: motor 21: shared shaft 21A: mounting portion 21B: mating coupling portion

21C: fitting 23: rotor 25: stator 27a, 27b: rolling bearing

30 pumping part 31 cylinder 31A bore 32 carrier

32b: fitting groove 32c: fitting hole 33: vane 34: power pin

35: first plate 36: second plate

40 sealing member 41 fixed seal 70 first buffer means 80 second buffer means

C: Combination S: Compression Space IG: Suction Clearance OG: Discharge Clearance

<Description of the reference numerals for the main components of the drawings of the third group (FIGS. 20 to 27)>

10: motor

11: shaft

12: rotor

12a: Core 12b: Magnet

13: stator 14: bearing

20 pumping part

21: cylinder

21a: Bore 21b: Recess

22: carrier

22a: shaft coupling portion 22b: fitting groove

22A: working fluid transfer means

23: vane

23a: curved portion 23c: complement euro

25, 26: 1st, 2nd plate

25a, 26a: depression 25b: hollow

HR: fixed rod

30, 30 ': body

30A: Motor Body

31: motor accommodating part 32: connector

30B: Pump Body

35: pump accommodation portion 36: suction port

37: outlet 38: annular projection

<Description of reference numerals for the main components of the drawings of the fourth group (FIGS. 28 to 32)>

10: motor unit

11: shaft

12: rotor

12a: Core 12b: Magnet

13: stator 14: bearing

R1, R2: retaining ring

20 pumping part

21: cylinder

21a: Bore 21b: Recess

22: carrier

22a: shaft coupling portion 22b: fitting groove

22c: fitting hole 22d: groove for reducing frictional resistance

22A, 22A '22A' ': working fluid transfer means

23: vane

23a: bend

24: electric spring 24A: electric pin

25, 26: 1st, 2nd plate

25a, 26a: depression 25b: hollow

HR: fixed rod

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

In describing the present invention with reference to the drawings, the basic principle is that the same reference numerals in each of the drawings, in particular, the tens and ones digits, or the tens, ones and digits have the same function as the members having the same function. In the drawings, unless otherwise specified, the members indicated by the reference numerals in the drawings may be regarded as members conforming to these standards.

However, the drawings of the first group of figures 1 to 11 relate to structures for damping the operating member, in particular the roller and for reducing the noise and friction of the carrier,

12 to 19 which relate to assembling the shaft after pre-assembling the pumping part by improving the structure of the shaft when the driving pin is introduced to improve the operation response in the operating member, particularly the vane type operating member . Drawing of the second group ,

The third of the actuating member, in particular in Fig. 20 related without a transmission means such as a motorized pin or transmission spring in the actuating member of the vane type the Com plug garment flow path, to ensure a sufficient response to that formed on both side surfaces of the vanes to 27 Military drawings ,

In the fourth group of FIGS. 28 to 32 related to the structure in which one plate is integral with the cylinder, reference numerals are irrelevant to each other, and the names of the components are also slightly different.

However, each feature of the first to fourth groups can be combined with each other, and the claims of the present invention also claim a combination of each feature.

Features associated with the drawings of the first group from FIG. 1 to FIG. 11 will be described.

According to the present invention, the suction direction of the working fluid, which is LPG, coincides with the rotational direction of the pump, and the pumping fluid is maintained by improving the suction efficiency while allowing the working fluid to pass through the pump to maintain the pump performance. As a pressurized pump,

Referring to FIG. 1, the configuration of the present invention will be described with reference to a flow chamber 110 that first sucks in a working fluid and discharges it to an engine, and a housing 120 that supplies rotational force to the flow chamber 110.

In the flow chamber 110, a pumping unit 140 for suctioning and discharging a working fluid by periodically changing a space volume is disposed, and an inlet 112a and an outlet 113a formed on the flow chamber 110. By this, a working fluid is introduced into and discharged from the pumping part 140. In addition, a housing 120 in which a motor for rotating the pumping part 140 is embedded is formed at one side of the flow chamber 110. By such a configuration, the suction direction of the working fluid coincides with the rotation direction of the pumping unit 140, thereby reducing the resistance of the flow to improve the suction efficiency.

In this case, the flow chamber 110 and the housing 120 are isolated from each other because the working fluid flowing by the pumping unit 140 is prevented from leaking into the housing 120.

Hereinafter, the pumping unit 140 will be described with reference to FIGS. 1 and 2.

The pumping part 140 has a carrier 142 disposed in a bore provided in the cylinder 144 and an actuating member, in particular a roller type actuating member 143 (hereinafter referred to as a 'roller') on the carrier 142. ) Is placed.

At this time, the fluid is sucked and discharged by the rotational movement of the carrier 142 and the roller 143.

At this time, the flow path of the suction and discharge working fluid is due to the first plate 141 and the second plate 145.

The first plate 141 and the second plate 145 have a similar shape, and protruding portions 141b and 145b protrude from the flat portions 141a and 145a in the shape of disks. The protruding portions 141b and 145b have a shape in which a circular or side surface protrudes in a fan shape at the center of the flat portions 141a and 145a (see "A" in FIG. 1, where "A" is a rear perspective view). However, in the center of the second plate 145, the rotating shaft through-hole 145c for penetrating the rotating shaft 121, which extends from the motor, is formed.

The fluid is transferred by the configuration of the pumping unit 140 as described above will be described in detail with reference to FIG.

FIG. 2 shows a carrier 142 mounted in the cylinder 144 to clearly display the working fluid flow therein with the first plate 141, the cylinder 144, and the second plate 145 assembled; The configuration of the roller 143 is omitted.

By the rotational movement of the carrier 142 and the roller 143, the working fluid is transferred between the flat portion 141a of the first plate 141 and the cylinder 144 and the flat portion 145a of the second plate 145. It is sucked through the suction gap I formed at one side between the cylinders 144 and discharged to the discharge gap O which is formed on the opposite side of the suction gap I.

The working fluid conveyed through the pumping unit 140 as described above is introduced through the inlet 112a as shown in FIG. 3. Thereafter, the working fluid is introduced into the pumping part 140 by the suction hole 112b formed at an upper side of the inner circumferential surface of the space 111 in which the pumping part 140 is accommodated and communicating with the suction port 112a. A discharge hole 113b is formed at one side of the suction hole 112b and communicated with the discharge hole 113a to be discharged.

As described above, the flow direction of the fluid is in contact with the rotational direction of the pumping part 140 by the configuration of the suction port 112a, the suction hole 112b, the discharge port 113a, and the discharge hole 113b. When the pumping part 140 is in contact with the flow direction becomes the same direction to improve the suction efficiency as described above.

Meanwhile, as described above, the flow chamber 110 and the housing 120 are separated from each other. At this time, the rotation shaft 121 connected to the pumping part 140 extends from the motor embedded in the housing 120. A rotating shaft through hole 115 is formed as shown in FIG. 3.

Since the working fluid flowing in the flow chamber 110 may leak into the housing 120 by the rotating shaft through hole 115, a sealing member 116 may be installed in the rotating shaft through hole 115 to prevent leakage. It is preferable to prevent it (see Fig. 4).

5 is a perspective view showing an example of the first buffer means in the pressure pump according to the present invention, Figure 6 is a perspective view showing another example of the first buffer means in the pressure pump according to the present invention, Figure 7 is a pressure according to the present invention Figure 8 is a perspective view showing an example of the second buffer means in the pump, Figure 8 is a perspective view showing another example of the second buffer means in the pressure pump according to the present invention, Figure 9 is a perspective view showing a knurled portion of the carrier in the pressure pump according to the present invention 10 is a side cross-sectional view showing an example of reducing means in the pressure pump according to the present invention, Figure 11 is a perspective view showing another example of reducing means in the pressure pump according to the present invention.

On the other hand, as shown in Figure 5 to 11, the pressure pump according to the present invention,

The first buffer means 300 for preventing collision noise between the roller 143 and the carrier 142 in contact with each other,

Referring to Figure 5, the first buffer means 300,

It consists of an elastic buffer member 310 surrounding the roller 143 or the placement area 142a in the carrier 142 relative to the roller 143 or both.

Preferably, the shock absorbing member 310 is easily fitted to the roller 143 using an elastic bushing, and the adhesive or high frequency heat fusion may be applied to the placement area 142a in the carrier 142. It is mounted through the mounting means of (see Figure 5).

The first buffer means 300 as another example,

6,

The buffer material layer 320 is coated with a buffer material on the roller 143 or the placement area 142a in the carrier 142 with respect to the roller 143 or both.

Preferably, the buffer layer 320 is formed by coating the buffer material on the roller 143 and the placement area 142a of the carrier 142 and then curing the coating to form a coating layer.

Meanwhile, referring to FIGS. 7 and 8,

Second buffer for preventing collision noise, which is composed of an inner buffer surface of the cylinder 144 or an outer buffer surface of the carrier 142 disposed thereon or both of the elastic buffer member 410 or a buffer material layer 420 coated with a buffer material. Further comprising means 400,

Here, the buffer member 410 and the buffer layer 420 is the cylinder 144, as described in detail the mounting and forming process of the buffer member 310 and the buffer layer 320 of the first buffer means 300. And the carrier 142 is also mounted and formed.

Therefore, the first buffering means 300 and the second buffering means 400 by alleviating the impact between the contact portion, thereby can be expected to the effect that can prevent the impact noise.

Meanwhile, referring to FIG. 9, the outer circumferential surface of the carrier 142 is provided with a knurling part 500 for reducing friction load with the cylinder 144 and minimizing a gap therebetween.

In addition to reducing the frictional load generated when rotating in the bore of the cylinder 144 through the knurling portion 500, minimizing the coupling gap between the two to prevent the leakage of the working fluid to improve the performance of the pressure pump You can expect.

As shown in FIG. 9, the knurling part 500 has a shape in which comb patterns cross each other, or is composed of another example knurling part 500 ′ having threads formed along an outer circumferential surface thereof.

Meanwhile, referring to FIGS. 10 and 11,

The present invention includes an abatement means 600 for reducing frictional resistance between the first and second plates 141 and 145 and the carrier 142.

Friction resistance is generated between the carrier 142 and the interposing surfaces of the first and second plates 141 and 145 to reduce the performance of the pressure pump.

In order to solve this, there is a need for the reduction means 600,

The reduction means 600 is formed by forming a first recess 610 in a contact area of the carrier 142 with respect to the first and second plates 141 and 145.

As another example, the reducing means 600 includes a second recess 620 formed in a contact area between the first and second plates 141 and 145 with respect to the carrier 142.

That is, in the present invention, the first recess 610 having a predetermined depth may be formed on the upper and lower surfaces of the carrier 142, or the carriers 145b may be formed at the protrusions 145b of the first and second plates 141 and 145. The second recess 620 may be formed in each area corresponding to the contact portion with the 142.

Therefore, the contact area between the first and second plates 141 and 145 and the carrier 142 is reduced through the first recess 610 or the second recess 620, which is the reduction means 600. By reducing it, a reduction in frictional resistance can be expected.

Next  Features related to the drawings of the second group from 12 to 19 will be described.

In describing the pressure pump P according to the present invention, the direction reference is specified.

First, in FIG. 12 and FIG. 13, the side where the motor 20 is arranged is set to the front or the front side, and the side having the pumping unit 30 is set to the rear or the rear side,

Next, in FIG. 13, a direction in which the fitting groove 32b is formed based on the shaft coupling portion 32a of the carrier 32 embedded in the cylinder 31 having the bore 31A eccentric with respect to the shared shaft 21 is shown. The radial direction or the outer side is set, and the opposite shaft coupling portion 32a side is set as the center or the inner side.

First, as shown in FIGS. 12 and 13, the pressure pump P according to the present invention is largely a motor 20 including a rotor 23 and a state 25, and the motor 20 and a shared shaft ( 21 are shared and arranged in the bore 31A of the cylinder 31 so that the actuating member, in particular the vane type actuating member 33 (hereinafter referred to as 'vane'), is in the outer and inner sides, ie in the radial direction. Pumping unit 30 is provided with a carrier 32 for the appearance of the linear movement, and the first receiving unit 11 and the second receiving unit 13 for the motor 20 and the pumping unit 30 It has a housing 10 having.

As such, a basic feature of the pressure pump P according to the present invention is that the motor 20 and the pumping part 30 are provided in one housing 10 and share one shared shaft 21. ,

Therefore, it is sufficient if two rolling bearings 27a and 27b for supporting the shared shaft 21 are provided at both ends of the shaft, and the number of other parts is also reduced, so that the assembly is easy and the durability can be expected to increase.

Furthermore, by introducing the appropriate sealing member 40, the pressure pump P according to the present invention can be arranged in a form orthogonal to the direction of gravity, as well as being installed in a direction parallel or inclined with respect to the direction of gravity. The advantage is that the use can be further extended.

In the pressure pump (P) of the present invention, the housing (10) is the front first receiving portion (11) for the motor (20), the rear second receiving portion (13) for the pumping portion (30). In addition, a boundary portion 12 is provided between the first and second accommodating portions 11 and 13 and the sealing member 40 is arranged on an inner circumferential surface thereof, and an inner space of the housing 10 (the first accommodating portion). (11) -boundary portion 12-second receiving portion 13] may be appropriately selected depending on the purpose of use and the pump capacity.

12 to 14, the front end of the first accommodating part 11 and the rear end of the second accommodating part 13 in the housing 10. ) Cover 11a and 13a, respectively,

The cover 11a (hereinafter referred to as the shear cover) arranged at the front end of the first accommodating part 11 is screwed to the flange of the first accommodating part 11, and the second The cover 13a (hereinafter referred to as' rear cover ') arranged at the rear end of the receiving portion 13 is arranged in the release preventing ring groove 13c' and then fixed by the stop ring 13c, In addition, the covers 11a and 13a are respectively prevented from leaking or invading the fluid by the O-rings 11b and 13b.

The outer diameter of the rear end cover (13a) is smaller than the inner diameter of the rear end jaw forming the departure prevention ring groove (13c '), larger than the inner diameter of the front jaw can be arranged in the correct position,

The stop ring (13c) is narrowed in diameter due to its unique elasticity and cuts, that is, when the pressure is released into the annular groove (13c ') after being released, the diameter is expanded again to the rear end of the annular groove (13c') When the thickness of the rear cover 13a and the stop ring 13c is added together, the rear cover 13a and the stop ring 13c are prevented from shaking while being mounted corresponding to the width of the annular groove 13c '. do.

Next, the housing 10 has a suction port 15 and a discharge port 17 through which the fluid is sucked and discharged in a tangential direction with respect to the rotational direction of the shared shaft 21, as can be seen in FIG. 15B, The suction passage 15a and the discharge passage 17a which are connected to the suction port and the discharge port are communicated with the second receiving portion 13, and the suction passage and the discharge passage respectively have a [cylinder ( 31)-the first plate 35-the second plate 36, the combination (C)] through the suction gap (IG) and the discharge gap (OG) so that the fluid can enter and exit the substantially compressed space (S) In communication.

Subsequently, the motor 20 is arranged on the outer circumferential surface of the shared shaft 21 and the outer circumferential surface of the rotor 23 and fixed to the inner circumferential surface of the first accommodating portion 11 of the housing 10. It consists of a stator 25 and rolling bearings 27a and 27b which support both ends of the shared shaft 21.

The sharing shaft 21 may be arbitrarily divided into a section for the motor 20 and a section for the pumping unit 30. In particular, the rear side of the sharing shaft 21 is the sealing member 40 and the first. It may be divided into a mounting portion 21A for the plate 35 and a corresponding coupling portion 21B for the coupling portion 32a of the carrier 32.

At this time, the corresponding coupling portion 21B is easily coupled to the driving pin 34 (which can be replaced by an electric spring, more comprehensively referred to as a transmission means) coupled to the carrier 32. The fitting portion 21C opened toward the upper surface is formed so that the driving pin 34 can be easily coupled to the shared shaft 21 in a state of being fitted into the fitting hole 32c of the carrier 32.

The fitting of such a transmission means and the shaft may be introduced for the roller type operating member shown in the drawing of the first group.

In other words, the fitting portion 21C formed in the corresponding coupling portion 21B of the shared shaft 21 is coupled to the fitting hole 32c of the carrier 32 to allow the opposite vanes 33 to interlock linearly. Comprising a structure corresponding to the coupling structure of the driving pin 34, the driving pin 34 exposed to the shaft coupling portion 32a when the shared shaft 21 is inserted into the shaft coupling portion 32a of the carrier 32. ) Is placed in the fitting portion (21C) can be easily coupled.

In addition, the fitting portion 21C is formed to correspond to the number and the coupling direction of the power pin 34 is settled can correspond to the number and coupling structure of the power pin is properly selected according to the purpose of use and pump capacity. It is more extensible.

Looking at the coupling method of the shared shaft 21 and the pumping unit 30, more precisely the carrier 32, after inserting all the transmission pins 34 and vanes 33 are inserted into the carrier 32 and the carrier The 32 is arranged in the cylinder 31, the first plate 35 and the second plate 36 are combined to form a pumping unit 30, and then inserted into the shared shaft 21.

That is, as the coupling method of the shaft and the carrier, which was proposed in the related art (Patent No. 037363684), solves the inconvenience of assembling the insertion of the power pin into the through hole formed in the shaft after the coupling of the shaft and the carrier.

The coupling is completed by inserting the pre-assembled pumping unit 30 into the shared shaft 21 to obtain the ease of coupling compared to the conventional structure of the shaft and carrier, and the shared shaft 21 and the carrier ( 32) It is easy to assemble and disassemble to assemble, and it has advantages such as shortening of assembly time and easy maintenance.

As shown in Figs. 15A, 4B and 16, when a pair is provided in the direction in which the coupling structure of the transmission pin 34 crosses (Figs. 15A and 15B), the fitting portion 21C corresponds to this. It is formed to open toward the upper surface in the crossing direction,

When the driving pin 34 is coupled to the carrier 32 one by one interlocking linear movement of the vanes 33 of the opposite side (Fig. 16), the fitting portion 21C is made correspondingly and open to the upper surface Is formed.

The fitting portion 21C has solved the problem that the electric pin coupling portion formed in the conventional sharing shaft is penetrated at a predetermined position of the corresponding coupling portion 21B of the sharing shaft and thus is difficult to assemble. The sharing shaft according to the present invention is a carrier The power pin 34 exposed to the shaft coupling portion 32a of the carrier 32 when it is inserted in is naturally placed in the fitting portion 21C of the shared shaft 21 to facilitate assembly.

On the other hand, in Figure 14 (A) it is possible to check the cable (W) for the electrical introduction and on / off and other control signal transmission for the motor 20.

12, 13, 15a and 15b, looking at the pumping unit 30 arranged in the second receiving portion 13 of the housing 10,

In the present invention, the shared shaft 21 is not eccentrically rotated so that the compression space is moved and the volume of the compression space is changed so that the fluid is sucked and discharged,

Since the bore 31A of the cylinder 31 has a space eccentric with respect to the shared shaft 21, the volume change occurs.

The carrier 32 embedded in the bore 31A of the cylinder has a smaller diameter than the bore of the cylinder in order to secure the compression space S. In other words, the carrier 32 and the fitting groove 32b of the carrier 32 If the fitting holes 32c and the recesses 32d are ignored, the volume formed by the outer line of the carrier is smaller than the volume formed by the bore when the openings at both ends of the bore 31A of the cylinder 31 are blocked. .

In addition, a shaft coupling portion 32a is formed at the center of the carrier 32. The coupling portion 32a forms a non-circular shape for preventing idling, and the corresponding coupling portion 21B of the shaft is also formed. Have a corresponding shape.

Next, the carrier 32 is formed with radially symmetrical fitting grooves 32b (four in FIGS. 4A and 4B and two in FIG. 5), and the coupling portion 32a. Fitting holes 32c are formed through the two fitting grooves 32b on the opposite side, respectively.

A vane 33 is arranged in each fitting groove 32b of the carrier 32. A curved portion 33a is formed on the outer side of the vane, so that the inner surface of the cylinder 31 has a bore 31A. To reduce friction with

The function for reducing the frictional resistance is also achieved by the frictional resistance reduction symmetric groove 32d formed on both front and rear sides of the carrier 32,

The groove 32d may also serve to lose weight, and may be formed on the front side or the rear side of the carrier, or both, as necessary.

In the present invention, the groove 32d is formed on both front and rear surfaces of the carrier 32, so as to maintain an optimal balance during the rotation of the carrier 32.

On the other hand, it is provided with a driving pin 34 is located in the fitting hole (32c) of the carrier 32 so that the vanes 33 located opposite to each other to perform a linear interlocking movement,

In the state in which the driving pin 34 is fitted in the fitting hole 32c, the opposite vanes 33 are pressed to perform the interlocking linear motion, and the driving pin 34 is formed at the center of the carrier 32 by the shaft coupling part. In the state exposed to 32a, it is settled and fixed to the fitting part 21C of the shared shaft 21. FIG.

Since the driving pins 34 are formed in a pair, the fitting holes 32c are circular, and the fitting holes 32c are two pairs in total as shown in FIG. 15A and the driving pins 34 are two, It is possible to be arranged in a state in which the cut face is in contact with each other, the driving pins 34 are in close contact with the front and rear edges of the fitting hole.

As shown in FIGS. 15A, 15B, 16 and 17 (only reference numerals differ from FIG. 2 in the drawings of the first group), the first and second plates 35 and 36 are arranged in the eccentric bore 31A. As the carrier 32 is rotated by the rotation of the shared shaft 21 of the motor 20 in the combination C formed by the cylinder 31 and the cylinder 31, the vanes 33 are basically formed by centrifugal force. The curved portion 33a is always in contact with the inner surface of the bore 31A, and the wandering of the vanes 33 (the operating state exiting from the fitting groove 32b) in accordance with the circular motion of the carrier 32 is linear. Therefore, any one vanes 33 and the other vanes disposed opposite to each other are symmetrically arranged on the carrier 32, so that the inner surfaces of the vanes 33 are supported by one driving pin 34.

When one vane is concealed inside the carrier fitting groove 32b, the driving pin 34 is pushed along, and the other vane on the opposite side is exposed to the outside to form a mutually interlocked structure. Since the responsiveness is improved, the suction and discharge forces for the fluid are enhanced.

In FIG. 15A, the first plate 35 closely arranged on the front surface of the carrier 32 is provided with a hollow 35C into which the shaft 21 is inserted, and has two symmetric recesses 35A and 35B [ In particular, the fan shape] is formed in the rear,

The second plate 36 closely arranged on the rear surface of the carrier 32 also has two symmetrical depressions 35A and 35B formed at the front,

As shown in FIGS. 15B and 17, the combination C (cylinder 31, first plate 35, and second plate) is rotated in accordance with the rotation of the shared shaft 21 of the motor 20 in the pumping unit 30. (36)] while the carrier 32 is rotated in the compression space (S) of the vane 33 has a linear movement,

Accordingly, the compression space formed by the inner and outer surfaces of the cylinder, the outer surface of the carrier, the first and second plates provided at the front and rear of the cylinder, and the two vanes are moved, and the volume of the compression space is changed to generate the suction discharge force of the fluid. ,

Pressure is exerted through the suction gap IG and the discharge gap OG of the assembly C, and then through the suction path 15a and the discharge path 17a of the housing 10 and eventually the suction port 15 and the discharge port. Since pressure acts up to (17), suction and discharge of fluid occur.

In addition, a contact groove 35B for the rotary seal 43 of the sealing member 40 to be described later is formed on the front surface of the first plate 35, the cover (on the back of the second plate 36) The ring groove 36b to which the O-ring 13b is coupled is formed for the sealing property of 13a).

Each of the [cylinder 31, first plate 35, and second plate 36] has pin insertion grooves 31 a, 35 a, and 36 a formed at an upper portion thereof. 10, the suction gap IG and the discharge gap OG coincide with the suction path 15a and the discharge path 17a, respectively, and the cylinder 31 A thicker portion of) will be placed on top to ensure that the bore 31A is properly aligned.

Subsequently, in the present invention, the mounting portion of the shared shaft 21 in the bearing 27b located at the rear side and the first plate 35 of the pumping part so as to separate the motor 20 and the pumping part 30 from the fluid. A sealing member 40 coupled to 21A and positioned at the boundary 12 of the housing 10 is provided.

In particular, it consists of a mechanical seal, so that the pumping fluid can withstand strong acids, strong salts, or flammable fluids such as LLP and LENG for a long time, and it is desirable to eliminate the risk of motor damage, fire, or explosion due to leakage of the fluid. .

The sealing member 40 is also composed of a fixed seal 41 is fixed to the inner peripheral surface of the boundary portion 12 of the housing 10 and a rotary seal 43 is fixed to the outer peripheral surface of the shared shaft 21, respectively Source leakage is prevented between the shaft 21 and the rotary seal 43 and between the inner wall of the boundary portion 12 and the fixed seal 41, and between the fixed seal 41 and the rotary seal 43 is independent. Can be filled with

In particular, the fixing of the rotary seal 43 is made by a snap ring 45 (see FIGS. 12 and 13) connecting the rotary seal 43 and the shared shaft 21 to increase the assemblability and easy disassembly. Ease of maintenance can be guaranteed.

Furthermore, as shown in FIGS. 18 and 19 (only reference numerals differ from those in FIGS. 6 and 7 in the drawings of the first group), collision noise between the vanes 33 and the contact portions of the carriers 32 is mutually different. The first shock absorber 70 is provided to prevent the collision noise generated during operation.

The first buffer means 70 is made of an elastic member 71 surrounding the vane 33 or the fitting groove 32b of the carrier 32 with respect to the vane 33 or both thereof, preferably The elastic member 71 is easily fitted to the vane 33 by using an elastic bushing, and the mounting groove 32b of the carrier 32 has a mounting means such as adhesive or high frequency heat fusion. Through the mounting.

At this time, the vane 33 may be formed in a cylindrical shape to reduce impact noise, and the shape of the fitting groove 32b of the carrier 32 may also be formed in a corresponding shape.

In addition, as another embodiment of the first buffering means 70, a buffer layer 72 coated with a cushioning material is formed on the fitting groove 32b of the vanes 33 or the carrier 32, or both. The buffer layer 72 may be formed by applying a buffer paint to the fitting grooves 32b of the vanes 33 and the carrier 32 and then drying and curing to form a coating layer.

On the other hand, a collision made of an elastic buffer member 81 that covers the inner circumferential surface of the bore 31A of the cylinder 31 or the outer circumferential surface of the carrier 32 or both disposed therein or a buffer material layer 82 coated with a cushioning material. The second cushioning means 80 for preventing noise is further provided,

Here, the buffer member 81 and the buffer layer 82, which is the second buffer means 80, are installed and formed of the elastic member 71 and the buffer layer 72 of the first buffer means 70 described above. According to the method is mounted and formed on the cylinder 31 and the carrier 32.

Therefore, the first buffering means 70 and the second buffering means 80 is to mitigate the impact between the contact portion, thereby the effect that can be expected to prevent the impact noise.

Next  Features related to the drawings of the third group from 20 to 27 will be described.

As shown in Fig. 20 to 27, the improved pressure pump for interlocking linear motion of the operating member, in particular the vane type operating member (hereinafter referred to as 'vane') according to the present invention,

The motor 10 and the pumping unit 20 is divided into two types of separate and integral.

23 and 24,

A motor 10 comprising a shaft 11, a rotor 12, a stator 13, and a bearing 14 is provided, which is a unitary structure,

20 to 22,

In the separate type, the motor 10 including the shaft 11, the rotor 12, the stator 13, and the bearing 14, and a corresponding shaft 11A connected to the shaft 11 include the pumping part 20. It is made to be provided.

The rotor 12 is arranged on the outer circumferential surface of the shaft 11 and includes a core 12a embedded therein and a magnet 12b surrounding the core 12a.

The stator 13 is made while covering the magnet 12b of the rotor 12.

Meanwhile, a pumping part 20 including a cylinder 21, a carrier 22, a vane 23, a first plate 25, and a second plate 26 is provided.

The cylinder 21 includes a bore 21a eccentrically formed at the center of the corresponding shaft 11A connected to the shaft 11 and recesses of the first and second plates 25 and 26 which will be described later on both sides. And a recess 21b corresponding to the portions 25a and 26a.

The carrier 22 is accommodated in the bore 21a of the cylinder 21 and is provided with a working fluid conveying means 22A for sucking and discharging the working fluid by turning the shaft 11.

The working fluid transfer means 22A,

Formed on the carrier 22, the corresponding shaft coupling portion 22a at the center so that one end of the corresponding shaft 11A is fitted, and fitting grooves 22b forming a symmetrical radial shape, It includes a fitting hole (22c) for connecting through the two fitting grooves (22b) located on the opposite side,

The vanes are positioned in the fitting grooves 22b of the carrier 22, respectively, and have a curved portion 23a formed on the outer surface thereof for surface contact with the inner surface of the bore 21a of the cylinder 21. 23 is provided.

At this time, the vane 23 and the contact surface of the fitting groove 22b of the carrier 22 is a linear movement of the vane 23 interlocked with the carrier 22 rotated by the corresponding shaft 11A. In addition, the vane 23 and the cylinder 21 further includes a complement flow path 23c for improving the contact force between the inner wall of the bore 21a.

Here, the complement flow path 23c is

Referring to Figure 25,

Entry part 23c-1 exposed from the fitting groove 22b when the vane 23 is released from the fitting groove 22b by centrifugal force and a working fluid is introduced thereto,

An entry portion 23c-2 in communication with a space from which the vane 23 has escaped, and

Distribution part 23c-3 connecting the entry part 23c-1 and the exit part 23c-2.

It is formed on both sides of the vane 23 to be in contact with the fitting groove (22b) of the carrier 22 is the working fluid is the entry portion (23c-1), the distribution portion (23c-3) and the exit portion ( After passing through 23c-2, the vanes 23 are pushed to the inner wall of the bore 21a of the cylinder 21.

The function of the complementary passage 23c may be replaced with the existing transmission means as described above (if necessary, the transmission means may be used together with the introduction of the complementary passage associated with the drawings of the third group). The vane 23 is to help the appearance of the linear movement, the most important point is provided for this function,

In the present invention, the complex passage 23c is formed on both the left and right sides of the vane 23 corresponding to the contact surface with the fitting groove 22b of the carrier 22.

Not limited to this, the first and second plates 25, which may be formed on the left side or the right side, or both of them, are not in contact with the fitting groove 22b of the carrier 22, that is, before and after. It can be formed on the front or rear or both of the vanes 23 corresponding to the contact with the surface 26, of course,

It may be formed jointly with the left and right sides of the vane 23,

In the present invention, each one of the complementary passages 23c is formed on both side surfaces of the vanes 23, but the present invention is not limited thereto, and one or more, that is, the plurality of complementary passages 23c may be formed. That is, the number of vanes 23 arranged in the fitting groove 22b of the carrier 22, the weight and size of the vanes 23, the rotational force of the motor, the diameter of the inlet 36 and the outlet 37, the cylinder 21 Optimum or maximum discharge with the pump in consideration of the configuration of the recess 21b space of the &lt; RTI ID = 0.0 &gt;) &lt; / RTI &gt; In view of the pressure, it is preferable to design the complex passage 23c.

Accordingly, the complex flow path 23c may vary in shape, position, number, etc. according to the intention of the designer, and a functional range of the complex flow path for replacing the existing transmission means, which is the most important point in the present invention. Various variations and modifications will be possible within the scope.

In one example, the complementary passage 23c may be introduced for the roller type operating member shown in the drawing of the first group.

The first plate 25 has a hollow 25b into which the corresponding shaft 11A is inserted and two symmetrical recesses 25a are formed at the rear, and the two recesses 25a are the cylinders 21. ) Is positioned to correspond to the recess 21b.

The second plate 26 has two symmetrical depressions 26a formed at the front side and is in close contact with the rear surface of the carrier 22. At this time, the two recesses 26a are positioned to correspond to the recesses 21b of the cylinder 21.

Here, the recesses 25a and 26a of the first and second plates 25 and 26 are arranged at positions biased to the upper side when the respective plates 25 and 26 are divided up and down, and are also arranged at an upper side. And a fluid suction and discharge mechanism at the inlet 36 and outlet 37 of the pump body 30B, which will be described later.

Alternatively, the depressions 25a and 26a of the first and second plates 25 and 26 are arranged laterally at the center when the plates 25 and 26 are divided up and down, and also arranged laterally at the center left and right. Fluid intake and discharge mechanisms at the inlet 36 and outlet 37 of the pump body 30B.

That is, the recess 21b of the cylinder 21 may have a structure arranged at a position biased to the upper side when the cylinder 21 is divided up and down, or a structure arranged at the center left and right, and accordingly the first Each recess 25a, 26a of the two plates 25, 26 is formed.

More preferably, in the arrangement structure in which the recess 21b of the cylinder 21 is biased in the upper portion, the first and second plates 25 and 26 may compensate for this by lowering the suction discharge pressure as compared with the structure arranged on the left and right of the center. Each recess 25a, 26a of the

In the structure arranged on the left and right of the center, the suction discharge pressure is high, and the recesses 25a and 26a of the first and second plates 25 and 26 do not need to be provided.

Therefore, each of the depressions 25a and 26a may be selected according to the suction discharge pressure and the characteristics of the pump.

Meanwhile, a half arc groove (not shown) penetrates through the cylinder 21 and the first and second plates 25 and 26 in a straight line, and a fixed rod HR is inserted into the half arc groove to allow the cylinder ( 21 and the first and second plates 25 and 26 are fixed to each other, and one end of the fixing rod HR is inserted and fixed to the inner wall of the pump body 30B to be described later.

In addition, the first and second plates 25 and 26 are formed with holes (not shown) into which the fixing rod HR and the auxiliary fixing rod (not shown) are inserted, respectively. It is inserted and fixed to the inner wall of 30B.

Meanwhile, referring to FIGS. 22 and 24,

Motor body (30A), comprising a pump body (30B), in the present invention, the motor body (30A) and the pump body (30B) is an integral pressure pump comprising a body (30) integrally,

And the motor body (30A) and the pump body (30B) is composed of a separate pressure pump including a body 30 made of a separate type.

First of all, in the integrated pressure pump,

The motor body 30A, the motor receiving portion 31 for the motor 10 is formed therein,

The pump body 30B has a pump receiving part 35 for the pumping part 20 formed therein, and an inlet for allowing fluid to be sucked and discharged in a tangential direction with respect to the rotational direction of the shaft 11 ( 36) and the outlet 37 is formed on one side.

On the other hand, in the separate pressure pump,

The motor body 30A may or may not be provided. First of all, the motor 10 and the pumping unit 20 should be separated.

Therefore, the pumping body 30B has a pump receiving part 35 for the pumping part 20 formed therein, and an inlet for allowing fluid to be sucked and discharged in a tangential direction with respect to the rotational direction of the shaft 11 ( 36) and the outlet 37 is formed on one side.

With the configuration as described above, look at the action state for the improved pressure pump for interlocking linear motion of the vane according to the present invention.

The carrier 22 is rotated in accordance with the rotation of the shaft 11 of the motor 10 in the assembly formed by the eccentric bore 21a and the first and second plates 25 and 26 and the cylinder 21. follow

Basically, since the curved portion 23a of the vane 23 always comes into contact with the inner surface of the bore 21a by centrifugal force, the vane 23 exits from the fitting groove 22b according to the circular motion of the carrier 22. Will be a linear movement,

At this time, the vane 23 escapes from the fitting groove 22b by centrifugal force through the complement flow path 23c formed in the vane 23, and a working fluid flows in, and the introduced working fluid flows into the entry part 23c. -1) and the space exiting through the distribution part (23c-3) and the exit part (23c-2),

That is, the vane 23 located in the fitting groove 22b of the carrier 22 is introduced into a space provided by linearly moving outward by centrifugal force,

The introduced working fluid pushes the rear surface of the vane 23, thereby assisting the vane 23 with the centrifugal force to move in and out.

In the pressurized pump, for the linear motion of the vane, it is possible to substitute for the use of electric means such as electric springs or electric pins.

Due to the operation of the electric springs or the power pins, noise, complex assembly and the resulting decrease in productivity can be expected.

And in order to enable the linear movement of the vanes 23 using only centrifugal force, there is a problem in that the weight of the vanes 23 needs to be increased.

Completion channel 23c in the present invention will be able to solve this problem.

Therefore, referring to FIGS. 26 and 27, each recess 25a, 26a of the first and second plates 25 and 26 located in communication with the suction port 36 and the recess 21b of the cylinder 21 are described. The working fluid introduced into the suction port 36 of the pump body 30B is in communication with the discharge port 37 of the pump body 30B by the volume change according to the linear movement of the vane 23 of the carrier 22. Each recess 25a, 26a of the first and second plates 25 and 26 located therein and the recess 21b of the cylinder 21 are moved, and the moved working fluid is discharged through the outlet 37.

Next  Features associated with the drawings of the fourth group from 28 to 32 will be described.

As shown in Figures 28 to 32, the integrated pump of the shaft through plate and the cylinder according to the present invention,

In particular, referring to FIG. 28,

A motor unit 10 including a shaft 11, a rotor 12, a stator 13, and a bearing 14 is provided, which will be described in detail.

The shaft 11 is a non-circular end, that is, to prevent the object coupled to one end from being idle, having a D-type shape, and formed with a through hole 15 formed therethrough. .

The rotor 12 is arranged on the outer circumferential surface of the shaft 11 and includes a core 12a embedded therein and a magnet 12b surrounding the core 12a.

The stator 13 is made while covering the magnet 12b of the rotor 12.

The bearing 14 supports both ends of the shaft 11, and is arranged at both ends of the shaft 11 with the rotor 12 and the stator 13 interposed therebetween, and the bearing 14 positioned at an upper end thereof. ) Is inserted into the lower surface of the motor cover 40 to be described later, the fixing ring (R1) for preventing the downward departure is fitted to the shaft 11, the bearing 14 located at the bottom of the motor body (to be described later) The fixing ring R2 is inserted into the bottom surface of 30A and inserted into the shaft 11 to prevent the upward departure.

On the other hand, the cylinder 21, the carrier 22, the actuating member, in particular the vane type actuating member 23 (hereinafter referred to as 'vane'), the electric spring 24 (a kind of transmission means), the first plate 25 ), And a pumping unit 20 including a second plate 26, which will be described in detail.

The cylinder 21 has a bore (21a) eccentrically formed at the center of the shaft 11 and recesses (25a, 26a) of the first and second plates (25, 26) to be described later on both sides. A corresponding recess 21b.

The carrier 22 is accommodated in the bore 21a of the cylinder 21 and is provided with a working fluid conveying means 22A for sucking and discharging the working fluid by turning the shaft 11.

The working fluid transfer means 22A as an example,

It is formed on the carrier 22, the shaft coupling portion 22a at the center so that one end of the shaft 11 is fitted, the fitting grooves 22b forming a symmetrical radial direction, and opposite sides It includes a fitting hole (22c) for connecting through the two fitting grooves (22b) located,

The vanes are positioned in the fitting grooves 22b of the carrier 22, respectively, and have a curved portion 23a formed on the outer surface thereof for surface contact with the inner surface of the bore 21a of the cylinder 21. 23 is provided,

In particular, referring to FIG. 28, vanes 23 located on opposite sides of the fitting holes 22c of the carrier 22 are configured to interlock linearly, and the fitting holes 22c of the carrier 22 are formed. An electric spring 24 is provided which sequentially inserts and distributes a distribution hole 15 formed at one end of the shaft 11 coupled to the shaft coupling portion 22a of the carrier 22.

In this case, in the structure in which the electric spring 24 is provided, two vanes 23 are applied.

As another example, the working fluid transfer means 22A ',

Referring to FIG. 29, two electric pins 24A having a semicircular cross-sectional shape except for the electric spring 24 are arranged alternately with each other, and the insertion hole 22c and the distribution hole 15 can be moved in and out. Four vanes 23 are applied in a structure in which one surface of the two driving pins 24A is arranged to abut each other.

At this time, the shaft 11 is preferably formed with two distribution holes 15A staggered to correspond to the two transmission pins (24A).

On the other hand, the working fluid transfer means 22A '' as another example,

A central shaft coupling portion 22a formed in the carrier 22, and radial fitting grooves 22b, and

And rollers 24B positioned in the fitting grooves 22b of the carrier 22 to perform linear motion.

On the other hand, the pump according to the present invention having the working fluid transfer means 22A, 22A ', 22A' 'as one or another example,

The cylinder 21 and the first plate 25 is made in one piece,

That is, the first plate 25 has a hollow 25b into which the shaft 11 is inserted and is integrally formed on the front surface of the cylinder 21 to be in close contact with the front surface of the carrier 22 accommodated in the bore 21a. It is made up of one.

Therefore, the reduction in the number of parts of the pump due to the integral of the cylinder 21 and the first plate 25, and through this can be expected the effect of assembly, productivity and cost reduction.

This first plate integrated cylinder structure can also be incorporated into pumps of the structure described in connection with the drawings of the first to third groups.

On the other hand, it further includes a reducing means 120 for reducing the frictional resistance between the first and second plates 25 and 26 and the carrier 22.

Friction resistance is generated between the carrier 22 and the interposing surfaces of the first and second plates 25 and 26 to reduce the performance of the pump.

In order to solve this, the need for the abatement means 120 is required.

The reduction means 120 includes a first recess 121 formed in a contact area of the carrier 22 with respect to the first and second plates 25 and 26.

As another example, the reduction means 120 ′ is formed by forming a second recess 122 in the close contact area of the first and second plates 25 and 26 with respect to the carrier 22.

That is, in the present invention, the first recess 121 having a predetermined depth may be formed on the front and rear surfaces of the carrier 22, or the front and rear of the carrier 22 in the first and second plates 25 and 26. The second recess 122 may be formed in an area in close contact with the surface.

Therefore, contact between the first and second plates 25 and 26 and the carrier 22 through the first recess 121 or the second recess 122, which is the abatement means 120 and 120 ′. By reducing the area, the reduction in frictional resistance and the smooth fluid suction and discharge improvement of the carrier 22 pivoting by the shaft 11 while minimizing the contact surface between the carrier 22 and the second plate 26 are achieved. You can expect

The first plate 25 has a hollow 25b into which the shaft 11 is inserted and two symmetrical depressions 25a are formed at the rear, and the two depressions 25a are formed in the cylinder 21. It is located in correspondence with the recess 21b.

The second plate 26 has two symmetrical depressions 26a formed at the front side and is in close contact with the rear surface of the carrier 22. At this time, the two recesses 26a are positioned to correspond to the recesses 21b of the cylinder 21.

Here, the recesses 25a and 26a of the first and second plates 25 and 26 are arranged at positions biased to the upper side when the respective plates 25 and 26 are divided up and down, and are also arranged at an upper side. And a fluid suction and discharge mechanism at the inlet 36 and outlet 37 of the pump body 30B, which will be described later.

Alternatively, the depressions 25a and 26a of the first and second plates 25 and 26 are arranged laterally at the center when the plates 25 and 26 are divided up and down, and also arranged laterally at the center left and right. Fluid intake and discharge mechanisms at the inlet 36 and outlet 37 of the pump body 30B.

That is, the recess 21b of the cylinder 21 may have a structure arranged at a position biased to the upper side when the cylinder 21 is divided up and down, or a structure arranged at the center left and right, and accordingly the first Each recess 25a, 26a of the two plates 25, 26 is formed.

More preferably, in the arrangement structure in which the recess 21b of the cylinder 21 is biased in the upper portion, the first and second plates 25 and 26 may compensate for this by lowering the suction discharge pressure as compared with the structure arranged on the left and right of the center. Each recess 25a, 26a of the

In the structure arranged on the left and right of the center, the suction discharge pressure is high, and the recesses 25a and 26a of the first and second plates 25 and 26 may not be provided.

Therefore, each of the depressions 25a and 26a may be selected according to the suction discharge pressure and the characteristics of the pump.

Meanwhile, a half arc groove (not shown) penetrates through the cylinder 21 and the first and second plates 25 and 26 in a straight line, and a fixed rod HR is inserted into the half arc groove to allow the cylinder ( 21 and the first and second plates 25 and 26 are fixed to each other, and one end of the fixing rod HR is inserted and fixed to the inner wall of the pump body 30B to be described later.

In addition, the first and second plates 25 and 26 are formed with holes (not shown) in which an auxiliary fixing rod (not shown) is inserted together with the fixing rod HR, and the auxiliary fixing rod is a pump to be described later. It is inserted and fixed to the inner wall of the body 30B.

On the other hand, in the working fluid transfer means 22A, 22A 'as an example and another example,

The second cushioning means 130 for preventing collision noise further comprising an elastic buffer member 131 covering the vane 23 or the fitting groove 22b or both, or a buffer layer 132 coated with a buffer material. It will be included.

And in the working fluid transfer means 22A '' as another example,

The second shock absorbing means 140 for preventing collision noise further comprising an elastic buffer member 141 covering the roller 24B or the fitting groove 22b or both, or a buffer material layer 142 coated with a buffer material. It will be included.

Here, preferably, the buffer members 131 and 141 are easily fitted to the roller 24B and the vane 23 by using elastic bushings, and the fitting grooves of the carrier 22 22b) is mounted through a mounting means such as pressure-sensitive adhesive or high frequency heat fusion (see FIGS. 31 and 6).

And, referring to Figure 32,

Instead of the buffer member 131, a buffer material layer 132 may be formed by coating and coating a buffer material. The coating layer is formed by applying a buffer material paint and then curing the same.

In the above description of the present invention, the pump has a specific shape and structure with reference to the accompanying drawings. Should be interpreted as belonging.

Claims (1)

A cylinder having an eccentric bore, a carrier disposed on the bore of the cylinder, a carrier for sucking and discharging a working fluid, and an operating member disposed within the carrier, and a working fluid disposed on the front side of the cylinder and suctioned A pumping part including a first plate providing a flow path of the cylinder and integrally coupled to the cylinder, and a second plate disposed at a rear side of the cylinder to provide a flow path for discharging the sucked working fluid; A flow chamber in which a working fluid flows in and out in a direction tangential to a rotation direction of the pumping part; And And a housing having a motor for supplying rotational force to the pumping unit and being partitioned with the flow chamber. A first recess formed in a contact region of the carrier with respect to the first and second plates and a contact region of the first and second plates with respect to the carrier to reduce frictional resistance between the first and second plates and the carrier; Reduction means including a formed second recessed portion, First buffer means for preventing collision noise is provided at the contact between the operating member and the carrier, Second buffer means for preventing collision noise is provided at the contact between the cylinder and the carrier, In order to reduce the frictional load between the carrier and the cylinder and to minimize a gap between the cylinders, a knurling part having a comb pattern cross-formed or threads formed along the outer circumferential surface is provided on the outer circumferential surface of the carrier, It further comprises a driving pin disposed in the carrier and for interlocking linear movement of the operating member on the opposite side, The shaft of the motor has a non-circular shape for preventing idling and is provided with a corresponding coupling portion inserted into the coupling portion formed in the carrier, The corresponding coupling part is formed with a fitting portion open toward the upper surface, the fitting portion is made of a structure corresponding to the coupling structure of the electric pin inserted into the carrier is pre-assembled the pumping part and then inserted into the shared shaft Pressurized pump, characterized in that the frictional resistance of the carrier is improved.