CN116816745A - Reciprocating motion device and striking hammer - Google Patents

Abstract

The application provides a reciprocating motion device and a striking hammer, wherein the reciprocating motion device comprises an oil cylinder assembly, an air cylinder assembly, a fixed shaft, a power output shaft and a hydraulic system, and the oil cylinder assembly and the air cylinder assembly are mutually independent; the oil cylinder assembly comprises an oil cylinder body, an oil cylinder piston rod and a first oil cavity which is arranged in the oil cylinder body and distributed on the side of the oil cylinder piston facing the oil cylinder piston rod; the cylinder assembly comprises a cylinder body, a cylinder piston rod and high-pressure air chambers which are arranged in the cylinder body and distributed on the side of the cylinder piston, which is opposite to the cylinder piston rod; the cylinder body and the cylinder body are fixedly connected through a fixed shaft, and the cylinder piston rod are fixedly connected through a power output shaft. The oil cylinder assembly and the air cylinder assembly are separately designed, so that the hydraulic oil cavity and the high-pressure air cavity are separated, particles worn in the high-pressure air cavity can be prevented from entering the hydraulic oil cavity, and the particles worn in the high-pressure air cavity can be effectively prevented from polluting hydraulic oil and even damaging a hydraulic system.

Description

Reciprocating motion device and striking hammer

Technical Field

The present application relates to a mechanical device, and more particularly, to a reciprocating motion device and a hammer equipped with the reciprocating motion device.

Background

At present, a plurality of reciprocating devices are used as oil cylinders, the piston rods of the oil cylinders can extend and retract back and forth from the cylinder bodies of the oil cylinders, and the piston rods of the oil cylinders drive other parts to move. Further, a piston fixedly connected with the piston rod is arranged in the inner cavity of the oil cylinder, a cavity of the inner cavity of the oil cylinder, which is at the side of the piston, facing away from the piston rod is an upper high-pressure air cavity, and a cavity of the inner cavity of the oil cylinder, which is at the side of the piston, facing towards the piston rod is a lower hydraulic oil cavity; after the piston reaches a preset position, the hydraulic oil in the hydraulic oil cavity is discharged, so that the high-pressure gas in the high-pressure air cavity expands to push the piston and the piston rod to move downwards, and the piston rod drives an object connected with the piston rod to reciprocate upwards and downwards. However, the cylinder of the above structure has the following drawbacks:

1. the piston rod occupies part of the area of the piston, so that the thrust area of the piston is small; if the falling speed needs to be increased, the pressure of the high-pressure gas needs to be increased, but the pressure is too high to burst easily.

2. The oil cylinder at the lower part of the piston has large area, large hydraulic oil mass and large instant oil discharge mass, so that the descending speed of the piston rod is slow.

3. The worn particles in the high-pressure air cavity can enter the hydraulic oil cavity through the piston to pollute hydraulic oil and damage a hydraulic system.

4. High-pressure oil is discharged to the oil tank rapidly, rubber impact on the inner wall of the oil pipe is large, friction resistance is large, and the falling speed of the piston rod is influenced.

Disclosure of Invention

In view of the above-mentioned drawbacks of the prior art, it is an object of the present application to provide a reciprocating device that separates a high-pressure air chamber from a hydraulic oil chamber, avoiding that the worn out particles in the high-pressure air chamber contaminate the hydraulic oil and even damage the hydraulic system.

In order to achieve the above object, the present application provides a reciprocating motion device, including an oil cylinder assembly, an air cylinder assembly, a fixed shaft, a power output shaft, and a hydraulic system, wherein the oil cylinder assembly and the air cylinder assembly are independent from each other; the hydraulic system comprises a hydraulic system, a hydraulic system and a hydraulic system, wherein the hydraulic system is characterized in that the hydraulic system comprises a hydraulic system, a hydraulic system and a hydraulic system, and the hydraulic system comprises an oil cylinder, an oil cylinder assembly, an oil cylinder piston movably arranged in the oil cylinder, an oil cylinder piston rod fixed with the oil cylinder piston, and a first oil cavity which is arranged in the oil cylinder and distributed on the side of the oil cylinder piston facing the oil cylinder piston rod along the moving direction of the oil cylinder piston; the cylinder assembly comprises a cylinder body, a cylinder piston movably arranged in the cylinder body, a cylinder piston rod fixed with the cylinder piston, and a high-pressure air cavity which is arranged in the cylinder body and is distributed on the side of the cylinder piston, which is opposite to the cylinder piston rod, along the moving direction of the cylinder piston; the cylinder body of the oil cylinder is fixedly connected with the cylinder body of the air cylinder through a fixed shaft, and the piston rod of the oil cylinder is fixedly connected with the piston rod of the air cylinder through a power output shaft.

Further, the oil cylinder piston and the oil cylinder piston rod are both in reciprocating translation along the up-down direction, and the oil cylinder piston rod extends downwards from the lower end of the oil cylinder body.

Further, the cylinder piston and the cylinder piston rod are both in reciprocating translation in the up-down direction, and the cylinder piston rod extends downwards from the lower end of the cylinder body.

Further, a second oil cavity which is distributed on the side of the oil cylinder piston, which is opposite to the oil cylinder piston rod, along the moving direction of the oil cylinder piston is also arranged in the oil cylinder body, and the second oil cavity is connected with a hydraulic system; when the first oil cavity discharges oil to the hydraulic system, the hydraulic system feeds oil to the second oil cavity.

Further, the hydraulic system comprises a hydraulic pump, an oil tank connected with the hydraulic pump and a first control valve group, wherein the first control valve group comprises a first valve body, a first connecting oil duct arranged in the first valve body, a first valve sleeve and a second valve sleeve both fixed in the first valve body, a first valve core movably arranged in the first valve sleeve and a second valve core movably arranged in the second valve sleeve, the first valve body is provided with a first oil duct and a second oil duct which are distributed in a staggered manner at the first valve sleeve and are communicated with the first connecting oil duct, the first valve body is provided with a third oil duct at the second valve sleeve, the first oil duct is connected with the first oil cavity, the second oil duct is connected with the hydraulic pump, and the third oil duct is connected with the second oil cavity;

when the cylinder piston rod, the cylinder piston rod and the power output shaft translate together along a first direction, the hydraulic pump feeds oil into the second oil passage opening, the first valve core is positioned at an opening position, the second oil passage opening is communicated with the first oil passage opening through a first connecting oil passage, and the second valve core is positioned at a closing position and is blocked between the third oil passage opening and the first connecting oil passage;

when the cylinder piston rod, the cylinder piston rod and the power output shaft translate together along a second direction opposite to the first direction, the first oil cavity discharges oil to the first oil channel, the first valve core is in a closed position and is blocked between the second oil channel and the first connecting oil channel, the second valve core is in an open position, so that the third oil channel is communicated with the first connecting oil channel, and the discharged oil at the first oil channel sequentially flows into the second oil cavity after passing through the first connecting oil channel and the third oil channel.

Further, the hydraulic system further comprises an electromagnetic reversing valve, a second control valve group and a one-way valve, the first valve sleeve is provided with a fourth oil port, the second valve sleeve is provided with a fifth oil port, the second control valve group comprises a second valve body, a second connecting oil duct arranged in the second valve body, a third valve sleeve fixed in the second valve body and a third valve core movably arranged in the third valve sleeve, the second valve body is provided with a sixth oil port and a seventh oil port which are distributed in a staggered manner at the third valve sleeve and are communicated with the second connecting oil duct, the third valve sleeve is provided with an eighth oil port, the hydraulic pump, the oil tank, the fifth oil port and the eighth oil port are all connected with the electromagnetic reversing valve, the third oil port and the second oil chamber are all connected with the seventh oil duct port, the third oil port and the sixth oil port are all connected with the oil tank, and the one-way valve is arranged on the connecting pipe between the third oil port and the oil tank and allows hydraulic oil at the third oil port to flow to the oil tank;

when the cylinder piston rod, the cylinder piston rod and the power output shaft translate along the first direction, the third valve core is positioned at an opening position, so that the sixth oil duct port and the seventh oil duct port are communicated through a second connecting oil duct;

when the cylinder piston rod, the cylinder piston rod and the power output shaft translate together along the second direction, the third valve core is in a closed position and is blocked between the seventh oil port and the second connecting oil duct.

Further, the first control valve group further comprises a first spring, the first valve sleeve comprises a first main body provided with a first through slideway and a first lantern ring provided with a first valve inner cavity, the first lantern ring extends out of the first main body, the first slideway is communicated with the first valve inner cavity, the fourth oil duct port is formed in the first lantern ring, the first valve core is movably assembled in the first slideway, and the first spring is positioned in the first valve inner cavity, and two ends of the first spring are respectively abutted against the first lantern ring and the first valve core; the first main body is located in the first connecting oil duct, a first groove and a first limiting surface which can be in butt fit with the first valve core are formed in the groove wall of the first slide way, a plurality of first oil holes are formed in the first main body, the first connecting oil duct is communicated with the first groove through the first oil holes, and the second oil duct is formed in the end portion of the first slide way.

Further, the first control valve group further comprises a second spring, the second valve sleeve comprises a second main body provided with a through second slideway and a second lantern ring provided with a second valve inner cavity, the second lantern ring extends out of the second main body, the second slideway is communicated with the second valve inner cavity, the fifth oil duct port is formed in the second lantern ring, the second valve core is movably assembled in the second slideway, and the second spring is positioned in the second valve inner cavity, and two ends of the second spring are respectively abutted against the second lantern ring and the second valve core; the second main body is located at the end part of the first connecting oil duct, a second groove and a second limiting surface which can be in butt fit with the second valve core are formed in the groove wall of the second slideway, a plurality of second oil holes are formed in the second main body, and the third oil duct port is communicated with the second groove through the second oil holes.

Further, the second control valve group further comprises a third spring, the third valve sleeve comprises a third main body provided with a through third slideway and a third lantern ring provided with a third valve inner cavity, the third lantern ring extends out of the third main body, the third slideway is communicated with the third valve inner cavity, the eighth oil duct port is formed in the third lantern ring, the third valve core is movably assembled in the third slideway, and the third spring is positioned in the first valve inner cavity, and two ends of the third spring are respectively abutted against the third lantern ring and the third valve core; the third main body is located in the second connecting oil duct, a third groove and a third limiting surface which can be in butt fit with the third valve core are formed in the groove wall of the third slide way, a plurality of third oil holes are formed in the third main body, the second connecting oil duct is communicated with the third groove through the third oil holes, and a seventh oil duct port is formed in the end portion of the third slide way.

Further, the application also provides a striking hammer which comprises a hammer head arm, a hammer head arranged on the hammer head arm and the reciprocating motion device, wherein the power output shaft of the reciprocating motion device is hinged with the hammer head arm.

As described above, the reciprocating motion device and the hammer according to the present application have the following advantageous effects:

according to the application, the first oil cavity in the oil cylinder assembly forms the hydraulic oil cavity of the oil cylinder assembly, the oil cylinder assembly and the air cylinder assembly are two mutually independent assemblies, and the two assemblies are separately designed, so that the hydraulic oil cavity in the oil cylinder assembly and the high-pressure air cavity in the air cylinder assembly are separated, and therefore, when the reciprocating motion of the power output shaft is realized, particles worn in the high-pressure air cavity can be prevented from entering the hydraulic oil cavity, the particles worn in the high-pressure air cavity can be effectively prevented from polluting hydraulic oil and even damaging a hydraulic system, and conversely, the particles worn in the hydraulic oil cavity can be prevented from entering the high-pressure air cavity, and the particles worn in the hydraulic oil cavity can be effectively prevented from damaging the air cylinder assembly.

Drawings

Fig. 1 is a schematic structural view of a reciprocating device in accordance with the present application, wherein a power take-off shaft translates in a first direction.

Fig. 2 is a schematic structural view of the reciprocating device in the present application, wherein the power output shaft translates in a second direction.

Fig. 3 is a diagram showing the connection relationship among the cylinder assembly, the stationary shaft and the power take-off shaft according to the present application.

Fig. 4 is a schematic structural diagram of a first control valve set according to the present application.

Fig. 5 is a schematic structural diagram of a second control valve set according to the present application.

Fig. 6 is a schematic structural view of the hammer of the present application.

Fig. 7 is a side view of fig. 6.

Description of element reference numerals

10. Fixed shaft

20. Power output shaft

30. Oil cylinder assembly

31. Cylinder body

32. Oil cylinder piston

33. Cylinder piston rod

34. First oil chamber

35. Second oil chamber

40. Cylinder assembly

41. Cylinder body

42. Cylinder piston

43. Cylinder piston rod

44. High-pressure air cavity

50. Hydraulic pump

60. Oil tank

70. First control valve group

71. First valve body

711. First connecting oil duct

712. First oil passage port

713. Second oil passage port

714. Third oil passage port

72. First valve sleeve

721. Fourth oil passage port

722. A first main body

723. First collar

724. First groove

725. First limiting surface

726. First oil hole

726. First oil hole

727. First slideway

73. Second valve sleeve

731. Fifth oil passage port

732. A second main body

733. Second collar

734. Second groove

735. Second limiting surface

736. Second oil hole

736. Second oil hole

737. Second slideway

74. First valve core

75. Second valve core

76. First spring

77. Second spring

80. Electromagnetic reversing valve

90. Second control valve group

91. Second valve body

911. Second connecting oil duct

912. Sixth oil passage port

913. Seventh oil passage port

92. Third valve sleeve

921. Eighth oil passage port

922. A third main body

923. Third collar

924. Third groove

925. Third limiting surface

926. Third oil hole

927. Third slideway

928. Third valve inner cavity

93. Third valve core

94. Third spring

110. One-way valve

120. Hammer arm

130. Hammer head

Detailed Description

Further advantages and effects of the present application will become apparent to those skilled in the art from the disclosure of the present application, which is described by the following specific examples.

It should be understood that the structures, proportions, sizes, etc. shown in the drawings are for illustration purposes only and should not be construed as limiting the application to the extent that it can be practiced, since modifications, changes in the proportions, or adjustments of the sizes, which are otherwise, used in the practice of the application, are included in the spirit and scope of the application which is otherwise, without departing from the spirit or scope thereof. Also, the terms such as "upper," "lower," "left," "right," "middle," and "a" and the like are used herein for descriptive purposes only and not for purposes of limitation, and are intended to limit the scope of the application as defined by the claims and the relative terms thereof as construed as corresponding to the claims.

The application provides a reciprocating motion device which is used for providing reciprocating motion power and driving other components to reciprocate. As shown in fig. 1 and 2, the reciprocating device according to the present application includes an oil cylinder assembly 30, an air cylinder assembly 40, a fixed shaft 10, a power output shaft 20, and a hydraulic system, the oil cylinder assembly 30 and the air cylinder assembly 40 being independent from each other. As shown in fig. 3, the oil cylinder assembly 30 includes an oil cylinder body 31, an oil cylinder piston 32 movably installed in the oil cylinder body 31, an oil cylinder piston rod 33 fixed to the oil cylinder piston 32, and a first oil chamber 34 provided in the oil cylinder body 31 and distributed on a side of the oil cylinder piston 32 facing the oil cylinder piston rod 33 in a moving direction of the oil cylinder piston 32, the first oil chamber 34 being connected to a hydraulic system and constituting a hydraulic oil chamber of the oil cylinder assembly 30. The cylinder assembly 40 includes a cylinder block 41, a cylinder piston 42 movably mounted in the cylinder block 41, a cylinder piston rod 43 fixed to the cylinder piston 42, and a high-pressure air chamber 44 provided in the cylinder block 41 and distributed on a side of the cylinder piston 42 facing away from the cylinder piston rod 43 in a moving direction of the cylinder piston 42. The cylinder body 31 and the cylinder body 41 are fixedly connected through the fixed shaft 10, the cylinder piston rod 33 and the cylinder piston rod 43 are parallel, the cylinder piston rod 33 and the cylinder piston rod 43 are fixedly connected through the power output shaft 20, and the fixed shaft 10 and the power output shaft 20 are parallel.

In the reciprocating motion device, when oil is supplied to the first oil cavity 34 of the oil cylinder assembly 30 by the hydraulic system, the oil cylinder piston 32 is pushed to translate along the first direction, the first direction is the upper direction of the paper surface in the views shown in fig. 1 to 3, the oil cylinder piston 32 drives the oil cylinder piston rod 33 to translate along the first direction, the oil cylinder piston rod 33 drives the air cylinder piston rod 43 and the power output shaft 20 to translate along the first direction, the power output shaft 20 outputs power, and the air cylinder piston 42 translates along the first direction along with the air cylinder piston rod 43 to compress high-pressure gas in the high-pressure air cavity 44. When the cylinder piston rod 33, the cylinder piston rod 43 and the power output shaft 20 are operated together in the first direction to a set distance, the first oil chamber 34 returns oil to the hydraulic system, the high-pressure gas in the high-pressure gas chamber 44 expands rapidly, the cylinder piston 42 is pushed to translate in a second direction opposite to the first direction, the second direction is the lower direction of the paper surface in the views shown in fig. 1 to 3, the cylinder piston 42 drives the cylinder piston rod 43 to translate together in the second direction, and the cylinder piston rod 43 drives the power output shaft 20 to translate together with the cylinder piston rod 33 in the second direction, so that the power output shaft 20 outputs reverse power. Therefore, the reciprocating motion of the power output shaft 20 can be realized, the oil cylinder assembly 30 and the air cylinder assembly 40 are two mutually independent assemblies, and the two assemblies are separately designed, so that a hydraulic oil cavity in the oil cylinder assembly 30 is separated from a high-pressure air cavity 44 in the air cylinder assembly 40, and therefore, particles worn in the high-pressure air cavity 44 can be prevented from entering the hydraulic oil cavity, the particles worn in the high-pressure air cavity 44 can be effectively prevented from polluting hydraulic oil and even damaging a hydraulic system while the reciprocating motion of the power output shaft 20 is realized, and conversely, the particles worn in the hydraulic oil cavity can be prevented from entering the high-pressure air cavity 44, and the particles worn in the hydraulic oil cavity can be effectively prevented from damaging the air cylinder assembly 40.

Further, as shown in fig. 1 to 3, a second oil chamber 35 is further provided in the cylinder block 31 and distributed on the side of the cylinder piston 32 facing away from the cylinder piston rod 33 along the moving direction of the cylinder piston 32, and the second oil chamber 35 is connected to a hydraulic system; first oil chamber 34 and second oil chamber 35 in cylinder assembly 30 constitute the hydraulic oil chambers of cylinder assembly 30. When the cylinder piston rod 43 drives the power output shaft 20 and the cylinder piston rod 33 to translate along the second direction, the oil discharged from the first oil cavity 34 can be directly discharged to the hydraulic system, namely, the oil is directly discharged; or the discharged oil of the first oil cavity 34 flows back to the second oil cavity 35 under the action of the hydraulic system, so that the secondary utilization is realized. The oil discharge by the first oil chamber 34 is preferably secondarily utilized in this embodiment; specifically, when the first oil cavity 34 discharges oil to the hydraulic system, the hydraulic system feeds oil to the second oil cavity 35, so that the secondary utilization of hydraulic oil is realized; specifically, the secondarily-used hydraulic oil in the second oil chamber 35 is discharged from the first oil chamber 34. On the one hand, the cylinder piston 32 can be rapidly pushed to translate along the second direction, so that the cylinder piston rod 33, the cylinder piston rod 43 and the power output shaft 20 can accelerate to translate along the second direction; on the other hand, the hydraulic oil that enters the second oil chamber 35 is discharged from the hydraulic oil in the first oil chamber 34, and is reused as energy released by the hydraulic oil, so that energy can be effectively saved. Therefore, the reciprocating device related to the application is an energy-saving type rapid reciprocating device.

Further, both the cylinder assembly 30 and the cylinder assembly 40 are inverted structures in the present application. Specifically, as shown in fig. 1 to 3, in the cylinder assembly 30, the cylinder piston 32 and the cylinder piston rod 33 are reciprocally translated in the up-down direction, the cylinder piston rod 33 is fixed to the lower end surface of the cylinder piston 32, the first oil chamber 34 is located at the lower side of the cylinder piston 32, the second oil chamber 35 is located at the upper side of the cylinder piston 32, and the cylinder piston rod 33 protrudes downward from the lower end of the cylinder block 31. In this way, the cylinder piston rod 33 occupies a part of the volume in the first oil chamber 34, and during the up-and-down movement of the cylinder piston rod 33, the volume in the first oil chamber 34 is smaller than the volume of the second oil chamber 35, so that the oil quantity in the first oil chamber 34 is smaller than the oil quantity in the second oil chamber 35, and when the hydraulic oil flows back to the second oil chamber 35 for secondary use, the second oil chamber 35 can hold the hydraulic oil discharged from the lower first oil chamber 34, thereby ensuring the realization of secondary use of the hydraulic oil. In the cylinder assembly 40, both the cylinder piston 42 and the cylinder rod 43 are reciprocally translated in the up-down direction, the cylinder rod 43 is fixed to the lower end surface of the cylinder piston 42, the high pressure air chamber 44 is located at the upper side of the cylinder piston 42, and the cylinder rod 43 protrudes downward from the lower end of the cylinder block 41. Thus, the high-pressure gas in the high-pressure gas cavity 44 is sealed at the upper part of the cylinder piston 42, and only one piston leakage point is provided, so that the reliability is improved; meanwhile, a small amount of hydraulic oil is injected into the upper and lower cavities of the cylinder piston 42, which helps to reduce abrasion to the sealing members when the cylinder piston 42 and the cylinder rod 43 are rapidly dropped.

Preferably, as shown in fig. 3, the inner diameter of the cylinder body 31 is smaller than the inner diameter of the cylinder body 41, that is, the large-diameter cylinder body 41 and the small-diameter cylinder body 31 are matched, so that the pressure of high-pressure gas in the high-pressure gas cavity 44 can be reduced, and the safety is improved. In this embodiment, the high pressure gas in the high pressure gas chamber 44 is nitrogen.

Further, in order to enable the hydraulic oil in the first oil chamber 34 to flow back into the second oil chamber 35 for secondary use when the cylinder piston rod 33, the cylinder piston rod 43, and the power output shaft 20 move downward, the hydraulic system in the present application preferably adopts the following structure. As shown in fig. 1 and 2, and fig. 3 and 4, the hydraulic system includes a hydraulic pump 50, a tank 60 connected to the hydraulic pump 50, a first control valve group 70, a solenoid directional valve 80, a second control valve group 90, and a check valve 110. The first control valve group 70 includes a first valve body 71, a first connection oil passage 711 opened in the first valve body 71 and extending left and right, a first valve housing 72 and a second valve housing 73 both fixed in the first valve body 71, a first valve spool 74 mounted in the first valve housing 72 so as to be movable up and down, and a second valve spool 75 mounted in the second valve housing 73 so as to be movable left and right, a part of the first valve body 71 being located in a right-segment portion of the first connection oil passage 711, the second valve body 91 being provided at a left end of the first connection oil passage 711; the first valve body 71 has a first oil port 712 communicating with the first connection oil duct 711 on the right end side of the first valve housing 72, the first valve body 71 has a second oil port 713 communicating with the first connection oil duct 711 on the lower end side of the first valve housing 72, and the first valve body 71 has a third oil port 714 on the lower end side of the second valve housing 73; first port 712 is connected to first chamber 34, second port 713 is connected to hydraulic pump 50, and third port 714 is connected to second chamber 35; the upper end of the first valve housing 72 is provided with a fourth port 721 and the left end of the second valve housing 73 is provided with a fifth port 731. The second control valve group 90 includes a second valve body 91, a second connection oil duct 911 opened in the second valve body 91 and extending up and down, a third valve housing 92 fixed in the second valve body 91, and a third valve core 93 installed in the third valve housing 92 so as to be movable up and down, a part of the third valve body is located in the second connection oil duct 911, the second valve body 91 is opened with a sixth oil duct 912 communicating with the second connection oil duct 911 on the right side of the third valve housing 92, the second valve body 91 is opened with a seventh oil duct 913 communicating with the second connection oil duct 911 on the upper side of the third valve housing 92, and the lower end of the third valve housing 92 is opened with an eighth oil duct 921; the hydraulic pump 50, the oil tank 60, the fifth oil port 731 and the eighth oil port 921 are all connected to the electromagnetic directional valve 80, the third oil port 714 and the second oil chamber 35 are all connected to the seventh oil port 913, the third oil port 714 and the sixth oil port 912 are all connected to the oil tank 60, the check valve 110 is disposed on the connection line between the third oil port 714 and the oil tank 60, and the check valve 110 allows only the hydraulic oil at the third oil port 714 to flow to the oil tank 60. The second control valve group 90 and the check valve 110 can be used independently or together in the hydraulic system; when the second control valve group 90 and the check valve 110 are used independently, the discharged oil of the first oil cavity 34 directly flows back to the oil tank 60 through the check valve 110, and secondary utilization is not performed; when the two oil chambers are used together, the discharged oil of the first oil chamber 34 flows back to the second oil chamber 35 again under the action of a hydraulic system for secondary use. The second control valve group 90 and the check valve 110 can effectively prevent hydraulic oil or air sucked into the oil tank 60 due to the vacuum occurring in the second oil chamber 35 at the upper side of the cylinder piston 32 when the cylinder piston rod 33 falls.

Further, as shown in fig. 4, the first control valve group 70 further includes a first spring 76 extending vertically, the first valve housing 72 includes a first main body 722 provided with a first slide 727 penetrating vertically, and a first collar 723 provided with a first valve cavity 728, the first collar 723 integrally extends upward from an upper end of the first main body 722, the first slide 727 communicates with the first valve cavity 728, a fourth oil port 721 is provided at an upper end of the first collar 723, the first valve spool 74 is assembled in the first slide 727 so as to be movable vertically, the first spring 76 is located in the first valve cavity 728, and upper and lower ends of the first spring 76 are respectively abutted against the first collar 723 and the first valve spool 74. The first main body 722 is located in the first connecting oil duct 711, the first slide 727 is a part of the first connecting oil duct 711, the first main body 722 is provided with a first groove 724 on the groove wall of the first slide 727 and a first limiting surface 725 which can be in butt fit with the lower end of the first valve core 74, the first main body 722 is provided with a plurality of first oil holes 726, the first connecting oil duct 711 is communicated with the first groove 724 through the first oil holes 726, and the second oil port 713 is arranged at the lower end part of the first slide 727 and is communicated with the first groove 724.

Further, as shown in fig. 4, the first control valve group 70 further includes a second spring 77 extending in the left-right direction, the second valve housing 73 includes a second main body 732 provided with a second slide 737 penetrating in the left-right direction, and a second collar 733 provided with a second valve cavity 738, the second collar 733 integrally extends in the left direction from the left end of the second main body 732, the second slide 737 communicates with the second valve cavity 738, the fifth oil port 731 is provided on the left end surface of the second collar 733, the second valve spool 75 is assembled in the second slide 737 so as to be movable in the left-right direction, the second spring 77 is positioned in the second valve cavity 738, and both the left and right ends of the second spring 77 are respectively abutted against the second collar 733 and the second valve spool 75. The second main body 732 is located at the left end of the first connecting oil duct 711, the second main body 732 is provided with a second groove 734 and a second limiting surface 735 that can be in abutting engagement with the right end of the second valve core 75 on the groove wall of the second slideway 737, the second main body 732 is provided with a plurality of second oil holes 736, and the third oil hole 714 is communicated with the second groove 734 through the second oil holes 736.

Further, as shown in fig. 5, the second control valve group 90 further includes a third spring 94 extending vertically, the third valve sleeve 92 includes a third main body 922 provided with a third slide 927 penetrating vertically, and a third collar 923 provided with a third valve inner cavity 928, the third collar 923 integrally extends downwards from a lower end surface of the third main body 922, the third slide 927 is communicated with the third valve inner cavity 928, an eighth oil port 921 is provided on a lower end surface of the third collar 923, the third valve core 93 is assembled in the third slide 927 in a vertically movable manner, the third spring 94 is located in the first valve inner cavity 728, and upper and lower ends of the third spring 94 are respectively abutted against the third valve core 93 and the third collar 923. The third main body 922 is located in the second connecting oil duct 911, and the third slide 927 is a part of the second connecting oil duct 911; the third main body 922 is provided with a third groove 924 and a third limiting surface 925 which can be in abutting fit with the upper end of the third valve core 93 on the groove wall of the third slide 927, the third main body 922 is provided with a plurality of third oil holes 926, the second connecting oil duct 911 is communicated with the third groove 924 through the third oil holes 926, and the seventh oil duct 913 is arranged at the upper end and the lower end of the third slide 927 and is communicated with the third groove 924.

Preferably, in the first control valve group 70 and the second control valve group 90, the first valve core 74, the second valve core 75 and the third valve core 93 are concave bodies, that is, the portion of the first valve core 74 accommodating the first spring 76, the portion of the second valve core 75 accommodating the second spring 77 and the portion of the third valve core 93 accommodating the third spring 94 are hollow structures. More specifically, as shown in fig. 4 and 5, the lower end of the first spring 76 extends into the first valve element 74 to abut against the lower groove wall of the groove in the first valve element 74, the right end of the second spring 77 extends into the second valve element 75 to abut against the right groove wall of the groove in the second valve element 75, and the upper end of the third spring 94 extends into the third valve element 93 to abut against the upper groove wall of the groove in the third valve element 93.

The working principle of the energy-saving type rapid reciprocating motion device with the structure is as follows:

the power take-off shaft 20 moves up: as shown in fig. 1, the electromagnetic directional valve 80 is shifted to the oil intake position, and the high-pressure oil from the hydraulic pump 50 enters the second oil passage 713 and the electromagnetic directional valve 80 in two paths, respectively. After entering the first slideway 727, the hydraulic oil entering the second oil port 713 pushes the first valve core 74 upwards, so that the first valve core 74 moves upwards and is in an open position, the second oil port 713 is communicated with the first connecting oil duct 711, and then the hydraulic oil flowing from the second oil port 713 flows into the first oil cavity 34 after passing through the first slideway 727, the first connecting oil duct 711, the first groove 724, the first oil hole 726 and the first oil port 712, pushes the oil cylinder piston 32 and the oil cylinder piston rod 33 to move upwards, the oil cylinder piston rod 33 drives the power output shaft 20 to move upwards, and the power output shaft 20 drives the driven object, the air cylinder piston rod 43 and the air cylinder piston 42 to move upwards together, so that high-pressure gas in the high-pressure gas cavity 44 is compressed. The hydraulic oil entering the electromagnetic directional valve 80 flows into the fifth oil port 731 on the second valve sleeve 73, and pushes the second valve core 75 rightward after the hydraulic oil enters the second valve cavity 738, so that the first valve core 74 abuts against the second limiting surface 735 and is in the closed position, and the second valve core 75 seals between the first connecting oil duct 711 and the second groove 734, that is, the second valve core 75 seals between the third oil port 714 and the first connecting oil duct 711, and closes the third oil port 714. Meanwhile, the hydraulic oil in the second oil chamber 35 is discharged to the seventh oil port 913 by the upward movement of the cylinder piston 32, and enters the third slide 927 to push the third valve core 93 downward, so that the third valve core 93 is in the open position after downward movement, the sixth oil port 912 is communicated with the seventh oil port 913 through the second connecting oil duct 911, the hydraulic oil flowing in from the seventh oil port 913 flows back to the oil tank 60 through the second connecting oil duct 911, the third groove 924, the third oil hole 926 and the sixth oil port 912, and the hydraulic oil in the third valve inner chamber 928 flows back to the oil tank 60 through the eighth oil port 921 and the electromagnetic directional valve 80.

The power take-off shaft 20 moves down: as shown in fig. 2, after the cylinder piston rod 33, the cylinder piston rod 43, and the power output shaft 20 are moved up together by a set distance, the electromagnetic directional valve 80 is switched to the oil discharge position, and high-pressure oil from the hydraulic pump 50 is respectively introduced into the fourth oil passage 721 and the eighth oil passage 921 in two paths through the electromagnetic directional valve 80. The hydraulic oil flowing in from the fourth oil port 721 acts on the first valve element 74, and pushes the first valve element 74 downward, so that the first valve element 74 moves downward and abuts against the first limiting surface 725 to be in a closed position, and the first valve element 74 seals the lower end of the first slide 727, that is, between the second oil port 713 and the first connecting oil duct 711, so as to close the second oil port 713. When the hydraulic oil flowing in from the eighth port 921 acts on the third valve element 93 and pushes the third valve element 93 upward, the third valve element 93 moves upward and abuts against the third stopper surface 925 to be in the closed position, and the third valve element 93 closes the upper end of the third slide 927, that is, between the seventh port 913 and the second connection oil passage 911, to close the seventh port 913. Meanwhile, the high-pressure gas in the high-pressure air cavity 44 rapidly expands to push the air cylinder piston 42 and the air cylinder piston rod 43 to move downwards, the air cylinder piston rod 43 drives the power output shaft 20 to move downwards, the power output shaft 20 drives the driven object, the air cylinder piston rod 33 and the air cylinder piston 32 to move downwards together, the first oil cavity 34 discharges oil to the first oil port 712, the hydraulic oil flows into the first connecting oil duct 711 after passing through the first oil hole 726 and the first groove 724 to push the second valve core 75 leftwards, the second valve core 75 is left moved and then is in an open position, so that the third oil port 714 is communicated with the first connecting oil duct 711, the third oil port 714 is opened, the hydraulic oil discharged from the first oil port is returned to the second oil cavity 712 again, the energy released by the hydraulic oil pressure is reused, and the oil cylinder piston 32 is pushed to rapidly move downwards, namely the rapid downward movement of the power output shaft 20 is realized; the hydraulic oil in the second valve cavity 738 is released to the oil return tank 60 after passing through the fifth oil port 731 and the electromagnetic directional valve 80, and a part of the hydraulic oil discharged from the third oil port 714 is returned to the oil tank 60 through the check valve 110.

Thus, one quick reciprocating operation is completed.

Further, the present application provides a striking hammer including a hammer head arm 120, a hammer head 130 mounted to the hammer head arm 120, and the above reciprocating means, in which a power output shaft 20 is hinged to the hammer head arm 120, as shown in fig. 6 and 7. The hammer may be mounted in a variety of mechanical devices, and a part of the mechanical device for mounting the hammer is defined as a mount, and one end of the hammer head arm 120 is hinged to the mount of the mechanical device, and the stationary shaft 10 of the reciprocating means is hinged to the mount of the mechanical device, thereby mounting the hammer in the mechanical device. When the electromagnetic directional valve 80 is switched to the oil inlet position, the hydraulic system moves upwards to drive the power output shaft 20 and the cylinder piston rod 43 to move upwards together when the hydraulic system feeds oil into the first oil cavity 34, the power output shaft 20 drives the hammer head arm 120 to move upwards, and the hammer head arm 120 drives the hammer head 130 to move upwards together; when the electromagnetic directional valve 80 is switched to the oil discharging position after reaching the set position, the first oil cavity 34 discharges oil to the hydraulic system, the cylinder piston rod 43 moves downwards to drive the power output shaft 20 and the cylinder piston rod 33 to move downwards together, the power output shaft 20 drives the hammer head arm 120 to move downwards, the hammer head arm 120 drives the hammer head 130 to move downwards together, and the hammer head 50 forcefully hits an object downwards and then stops moving. And performing reciprocating operation in this way.

The hammer may be used alone, in which case the hammer head 50 directly strikes the object; alternatively, the hammer described above may be used in a breaking hammer, in which case the hammer head 50 strikes the shank of the breaking hammer.

In summary, the present application effectively overcomes the disadvantages of the prior art and has high industrial utility value.

The above embodiments are merely illustrative of the principles of the present application and its effectiveness, and are not intended to limit the application. Modifications and variations may be made to the above-described embodiments by those skilled in the art without departing from the spirit and scope of the application. Accordingly, it is intended that all equivalent modifications and variations of the application be covered by the claims, which are within the ordinary skill of the art, be within the spirit and scope of the present disclosure.

Claims (10)

1. A reciprocating motion device, characterized in that: the hydraulic system comprises an oil cylinder assembly (30), an air cylinder assembly (40), a fixed shaft (10), a power output shaft (20) and a hydraulic system, wherein the oil cylinder assembly (30) and the air cylinder assembly (40) are mutually independent; the oil cylinder assembly (30) comprises an oil cylinder body (31), an oil cylinder piston (32) movably arranged in the oil cylinder body (31), an oil cylinder piston rod (33) fixed with the oil cylinder piston (32), and first oil cavities (34) which are arranged in the oil cylinder body (31) and distributed on the side, facing the oil cylinder piston rod (33), of the oil cylinder piston (32) along the moving direction of the oil cylinder piston (32), wherein the first oil cavities (34) are connected with a hydraulic system; the cylinder assembly (40) comprises a cylinder body (41), a cylinder piston (42) movably arranged in the cylinder body (41), a cylinder piston rod (43) fixed with the cylinder piston (42), and high-pressure air chambers (44) which are arranged in the cylinder body (41) and distributed on the side, opposite to the cylinder piston rod (43), of the cylinder piston (42) along the moving direction of the cylinder piston (42); the oil cylinder body (31) and the air cylinder body (41) are fixedly connected through the fixed shaft (10), and the oil cylinder piston rod (33) and the air cylinder piston rod (43) are fixedly connected through the power output shaft (20).

2. The reciprocation device of claim 1 wherein: the oil cylinder piston (32) and the oil cylinder piston rod (33) are in reciprocating translation along the up-down direction, and the oil cylinder piston rod (33) extends downwards from the lower end of the oil cylinder body (31).

3. The reciprocation device of claim 1 wherein: the cylinder piston (42) and the cylinder piston rod (43) are reciprocally translated in the up-down direction, and the cylinder piston rod (43) extends downwards from the lower end of the cylinder body (41).

4. The reciprocation device of claim 1 wherein: a second oil cavity (35) which is distributed on the side of the oil cylinder piston (32) opposite to the oil cylinder piston rod (33) along the moving direction of the oil cylinder piston (32) is also arranged in the oil cylinder body (31), and the second oil cavity (35) is connected with a hydraulic system; when the first oil cavity (34) discharges oil to the hydraulic system, the hydraulic system feeds oil to the second oil cavity (35).

5. The reciprocation device of claim 4 wherein: the hydraulic system comprises a hydraulic pump (50), an oil tank (60) connected with the hydraulic pump (50) and a first control valve group (70), wherein the first control valve group (70) comprises a first valve body (71), a first connecting oil duct (711) formed in the first valve body (71), a first valve sleeve (72) and a second valve sleeve (73) both fixed in the first valve body (71), a first valve core (74) movably mounted in the first valve sleeve (72) and a second valve core (75) movably mounted in the second valve sleeve (73), the first valve body (71) is provided with a first oil port (712) and a second oil port (713) which are distributed in a staggered mode at the first valve sleeve (72) and are communicated with the first connecting oil duct (711), the first valve body (71) is provided with a third oil port (714) at the second valve sleeve (73), the first oil port (712) is connected with a first oil cavity (34), and the second oil port (713) is connected with the third oil port (35);

when the cylinder piston rod (33), the cylinder piston rod (43) and the power output shaft (20) translate together along a first direction, the hydraulic pump (50) feeds oil into a second oil port (713), the first valve core (74) is in an open position, the second oil port (713) is communicated with the first oil port (712) through a first connecting oil duct (711), and the second valve core (75) is in a closed position and is blocked between a third oil port (714) and the first connecting oil duct (711);

when the cylinder piston rod (33), the cylinder piston rod (43) and the power output shaft (20) translate together along a second direction opposite to the first direction, the first oil cavity (34) discharges oil to the first oil port (712), the first valve core (74) is in a closed position and is blocked between the second oil port (713) and the first connecting oil duct (711), the second valve core (75) is in an open position, the third oil port (714) is communicated with the first connecting oil duct (711), and the discharged oil at the first oil port (712) sequentially flows into the second oil cavity (35) after passing through the first connecting oil duct (711) and the third oil port (714).

6. The reciprocation device of claim 5 wherein: the hydraulic system further comprises an electromagnetic reversing valve (80), a second control valve group (90) and a one-way valve (110), a fourth oil port (721) is formed in the first valve sleeve (72), a fifth oil port (731) is formed in the second valve sleeve (73), the second control valve group (90) comprises a second valve body (91), a second connecting oil duct (911) formed in the second valve body (91), a third valve sleeve (92) fixed in the second valve body (91) and a third valve core (93) movably arranged in the third valve sleeve (92), a sixth oil port (912) and a seventh oil port (913) which are distributed in a staggered mode and are communicated with the second connecting oil duct (911) are formed in the third valve sleeve (92), an eighth oil port (921) is formed in the third valve sleeve (92), all the hydraulic pump (50), the oil tank (60), the fifth oil port 731 and the eighth oil port (921) are connected with the electromagnetic reversing valve (80), all the third oil port (714) and the seventh oil port (714) are connected with the third oil port (714) and the seventh oil port (714), the one-way valve (110) is arranged on a connecting pipeline between the third oil port (714) and the oil tank (60) and allows hydraulic oil at the third oil port (714) to flow to the oil tank (60);

when the oil cylinder piston rod (33), the air cylinder piston rod (43) and the power output shaft (20) translate together along the first direction, the third valve core (93) is in an opening position, and the sixth oil port (912) and the seventh oil port (913) are communicated through the second connecting oil duct (911);

when the cylinder piston rod (33), the cylinder piston rod (43) and the power output shaft (20) translate together along the second direction, the third valve core (93) is in a closed position and is blocked between the seventh oil port (913) and the second connecting oil duct (911).

7. The reciprocation device of claim 6 wherein: the first control valve group (70) further comprises a first spring (76), the first valve sleeve (72) comprises a first main body (722) provided with a first slide way (727) which penetrates through the first main body, and a first sleeve ring (723) provided with a first valve inner cavity (728), the first sleeve ring (723) extends out of the first main body (722), the first slide way (727) is communicated with the first valve inner cavity (728), the fourth oil port (721) is formed on the first sleeve ring (723), the first valve core (74) is movably assembled in the first slide way (727), and the first spring (76) is positioned in the first valve inner cavity (728) and two ends of the first spring are respectively abutted against the first sleeve ring (723) and the first valve core (74); the first main body (722) is located in the first connecting oil duct (711), a first groove (724) is formed in the groove wall of the first slideway (727), a first limiting surface (725) which is in butt fit with the first valve core (74) is formed in the first main body (722), a plurality of first oil holes (726) are formed in the first main body (722), the first connecting oil duct (711) is communicated with the first groove (724) through the first oil holes (726), and the second oil port (713) is formed in the end portion of the first slideway (727).

8. The reciprocation device of claim 6 wherein: the first control valve group (70) further comprises a second spring (77), the second valve sleeve (73) comprises a second main body (732) provided with a second slide way (737) which penetrates through the second main body, and a second sleeve ring (733) provided with a second valve inner cavity (738), the second sleeve ring (733) extends out of the second main body (732), the second slide way (737) is communicated with the second valve inner cavity (738), the fifth oil port (731) is formed in the second sleeve ring (733), the second valve core (75) is movably assembled in the second slide way (737), and the second spring (77) is positioned in the second valve inner cavity (738) and two ends of the second spring are respectively abutted against the second sleeve ring (733) and the second valve core (75); the second main body (732) is located at the end part of the first connecting oil duct (711), a second groove (734) and a second limiting surface (735) which can be in butt fit with the second valve core (75) are formed in the groove wall of the second slide way (737), a plurality of second oil holes (736) are formed in the second main body (732), and the third oil hole (714) is communicated with the second groove (734) through the second oil holes (736).

9. The reciprocation device of claim 6 wherein: the second control valve group (90) further comprises a third spring (94), the third valve sleeve (92) comprises a third main body (922) provided with a third slide way (927) which is communicated with the third main body, and a third sleeve ring (923) provided with a third valve inner cavity (928), the third sleeve ring (923) extends out of the third main body (922), the third slide way (927) is communicated with the third valve inner cavity (928), the eighth oil port (921) is formed in the third sleeve ring (923), the third valve core (93) is movably assembled in the third slide way (927), and the third spring (94) is positioned in the first valve inner cavity (728) and two ends of the third spring are respectively abutted against the third sleeve ring (923) and the third valve core (93); the third main body (922) is located in the second connecting oil duct (911), a third groove (924) and a third limiting surface (925) which can be in butt fit with the third valve core (93) are formed in the groove wall of the third slide rail (927), a plurality of third oil holes (926) are formed in the third main body (922), the second connecting oil duct (911) is communicated with the third groove (924) through the third oil holes (926), and the seventh oil port (913) is formed in the end portion of the third slide rail (927).

10. A percussion hammer comprising a hammer head arm (120) and a hammer head (130) mounted to the hammer head arm (120), characterized in that: the reciprocating device of any one of claims 1-9, wherein the power take-off shaft (20) is hinged to the hammer head arm (120).